CN221146617U

CN221146617U - User heat exchange device

Info

Publication number: CN221146617U
Application number: CN202322543853.7U
Authority: CN
Inventors: 刘雄; 刘珂; 刘砚; 乐文毅; 年卫琦; 惠芳芳
Original assignee: Individual
Current assignee: Individual
Priority date: 2022-10-06
Filing date: 2023-09-12
Publication date: 2024-06-14
Anticipated expiration: 2033-09-12
Also published as: CN117232035A

Abstract

The utility model discloses a user heat exchange device, which comprises a water supply pipe, a water distribution return pipe and a water source heat pump, wherein the water supply pipe is connected with the water source heat pump; the water source heat pump comprises a compressor, an evaporator, a condenser and a throttle valve; the outlet end of the compressor is connected with the inlet end of the compressor sequentially through the inlet end of the condenser refrigerant side, the outlet end of the condenser refrigerant side, the throttle valve, the inlet end of the evaporator refrigerant side and the outlet end of the evaporator refrigerant side to form a water source heat pump refrigerant circulation system; the water side inlet end of the evaporator is connected with the water supply pipe through the outlet end of the distribution water supply pipe and the inlet end of the distribution water supply pipe in sequence; the water side outlet end of the evaporator is connected with the water supply pipe through the inlet end of the distribution return pipe and the outlet end of the distribution return pipe in sequence. The method is characterized in that: the user heat exchange device supplies heat to the user heat exchange device in a centralized manner through a water supply pipe, and can supply cold for the user in a dispersed manner according to the needs of the user in summer, so that the city primary and secondary heat supply networks can realize large-temperature-difference centralized heat supply in winter.

Description

User heat exchange device

Technical Field

The utility model relates to a user heat exchange device, and belongs to the technical field of central heating.

Background

With the development of society and the improvement of living standard of people, the application of heating in winter of buildings or building communities by using a central heating system in cities is more and more widespread, and the central heating system commonly used at present is generally a double-pipe hot water heating system, as shown in fig. 8; as can be seen from fig. 8: the double-pipe hot water heating system consists of a heat source 1, a circulating pump 2, a heat user 3, a water supply pipe 4, a water return pipe 30, a distribution water supply pipe 6, a distribution water return pipe 7 and the like; the water supply pipe 4 and the water return pipe 30 are laid outdoors, commonly called: and (5) an outdoor pipe network.

In the working process, hot water produced by the heat source 1 is sent to each heat user 3 through the water supply pipe 4, enters the heat user 3 through the respective distribution water supply pipe 6 of the heat user 3, and after heat is released, the hot water with reduced temperature enters the water return pipe 30 through the respective distribution water return pipe 7 of the heat user 3; and then returns to the heat source 1 through the water return pipe 30 to be heated again under the action of the circulating pump 2; all heat consumers 3 are connected in parallel between the water supply pipe 4 and the return pipe 30 via their distribution water supply pipe 6, distribution return pipe 7.

In recent years, with the continuous expansion of urban scale, the heating radius of the urban central heating system is also continuously increased, which results in the increase of initial investment of the water supply pipe 4 and the water return pipe 30, and simultaneously, due to the increase of heating load, the pipe diameters of the water supply pipe 4 and the water return pipe 30 are also increased, so that the water supply pipe 4 and the water return pipe 30 are more difficult to lay in urban areas, because larger occupied area is needed; it is highly desirable to improve the ability of the water supply pipe 4 and the water return pipe 30 to transport heat at the same pipe diameter. In addition, in the northern cities which are heated in winter by using the urban central heating system in the traditional way, due to the increase of the heating area of the hot users in the original heating area of the heating system, the heating capacity of the original outdoor pipe network is insufficient, and the improvement of the heating capacities of the water supply pipe 4 and the water return pipe 30 is also highly hoped under the condition that the original outdoor pipe network is not changed; therefore, a large-temperature difference heating system that increases the temperature difference of hot water between the water supply pipe 4 and the water return pipe 30 has been receiving increasing attention from the heating industry in recent years.

Currently, for the central heating system shown in fig. 8, one solution for realizing large temperature difference heating is: one building type absorption heat exchanger unit 60 is added to the user introduction port of each heat user 3 in the system, as shown in fig. 9.

As can be seen from fig. 9: after adding a building type absorption heat exchanger unit 60 to the user inlet of each heat user 3, the user heat exchanger 50 of each heat user 3 at the user inlet is composed of the following parts: a water supply pipe 4, a water return pipe 30, a building type absorption heat exchanger unit 60, a distribution water supply pipe 6, a distribution water return pipe 7 and an indoor water pump 21.

Each heat consumer 3 in fig. 9 is connected in parallel to the water supply pipe 4 and the water return pipe 30 through the distribution water supply pipe 6 and the distribution water return pipe 7 of the consumer heat exchange device 50; and also belongs to a double-pipe hot water central heating system.

In the working process, hot water produced by the heat source 1 is sent to the user heat exchange device 50 of each heat user 3 through the water supply pipe 4, then enters the building type absorption heat exchange unit 60 of each user heat exchange device 50 through the distribution water supply pipe 6 of each user heat exchange device 50, drives the building type absorption heat exchange unit 60 to normally work by virtue of the hot water, heats the hot water sent to the indoor heat dissipation tail end 20 of the heat user through an indirect heat exchange mode (as shown in fig. 9), and after heat is released from the building type absorption heat exchange unit 60 and the water temperature is reduced, the hot water sent by the water supply pipe 4 enters the water return pipe 30 through the distribution water return pipe 7 of each user heat exchange device 50; the heat source 1 is returned to be heated again through the return pipe 30 by the circulation pump 2.

Under the action of the building type absorption heat exchanger unit 60 in the user heat exchange device 50, the temperature difference of hot water between the water supply pipe 4 and the water return pipe 30 in the scheme shown in fig. 9 can be greatly improved, so that the heat conveying capacity of the water supply pipe 4 and the water return pipe 30 in the scheme shown in fig. 9 can be increased under the condition of the same pipe diameter.

However, the user heat exchange device 50 using the building type absorption heat exchange unit 60 as a core shown in fig. 9 has the following problems in the actual operation process:

1) The outdoor pipe network is still a double pipe system, and has one water supply pipe 4 and one water return pipe 30, so that a larger floor area is still occupied when the city block is laid, and the initial investment and construction cost of the two pipes are still larger.

In addition, as shown in fig. 9, since the user heat exchange devices 50 of the heat users 3 are connected in parallel between the water supply pipe 4 and the water return pipe 30 through the water distribution pipe 6 and the water return pipe 7, it is known that this parallel connection manner can cause the hot water flows entering the user heat exchange devices 50 of the heat users 3 to affect each other when the heat source 1 delivers hot water to the user heat exchange devices 50 of the heat users 3 through the water supply pipe 4 and the water return pipe 30, so that the heat supply system generates hydraulic imbalance, thereby making the hot water flows entering some of the user heat exchange devices 50 insufficient and the hot water flows of some of the user heat exchange devices 50 excessive, thereby adversely affecting the normal operation of the building absorption heat exchanger unit 60 in the user heat exchange devices 50; affecting the normal operation of the large temperature difference heating system shown in fig. 9.

To solve the hydraulic imbalance of the solution shown in fig. 9, a plurality of regulating valves are added in each user heat exchange device 50, resulting in an increase of initial investment of the heating system; meanwhile, in order to ensure that the regulating and controlling valves function correctly in the actual operation of the heating system in the operation process, fine installation and debugging of installers and operators are extremely important besides relying on the correct design of designers, and the operation cost is increased.

2) In operation, the building type absorption heat exchanger unit 60 in each user heat exchange device 50 relies on hot water from the heat source 1 as driving energy, and in order to ensure the normal operation of the building type absorption heat exchanger unit 60, the requirement on the temperature of the hot water which enters the building type absorption heat exchanger unit 60 from the heat source 1 through the water supply pipe 4 is higher, and the temperature is generally about 90 ℃; meanwhile, after the backwater of the indoor heat dissipation end 20 is heated by the building type absorption heat exchanger unit 60, the temperature of the water supplied to the indoor heat dissipation end 20 cannot be higher than the temperature of the hot water in the water supply pipe 4; therefore, in practical engineering, the scheme shown in fig. 9 is unfavorable for recycling low-temperature waste heat at lower temperature, so that the low-temperature waste heat is used for central heating.

3) In summer, when the heat user 3 has a refrigeration requirement, the scheme shown in fig. 9 must produce hot water with higher temperature from the heat source 1, and then send the hot water to the user heat exchange device 50 of the heat user 3 having the refrigeration requirement through the water supply pipe 4 and the water return pipe 30; then, the building type absorption heat exchanger unit 60 in the user heat exchanger 50 is utilized to produce low-temperature chilled water for the indoor heat dissipation tail end 20 of the heat user, so that the city concentrated cooling is realized; however, in summer, it is known that heat users in the central heating system of the city have only a small number of central cooling demands, so the scheme shown in fig. 9 is not practical because of the small number of users and low cooling load when cooling in summer, and therefore, the energy consumption and the running cost are high.

In addition, when the above-mentioned user heat exchange device 50 becomes a heat station of an urban heat supply network, the building type absorption heat exchange unit 60 in the user heat exchange device 50 is used for replacing a plate heat exchanger in a conventional heat station to supply heat to a building district; the user heat exchange device 50 can realize large temperature difference operation from a primary network between a heat source of the urban heat supply network and each heating power station; but cannot simultaneously realize large temperature difference operation of the secondary network from the heating station to each building (i.e. the heat user 3) in the building cell.

Disclosure of Invention

The utility model aims to provide a water supply pipe for supplying heat, wherein the temperature of hot water in the water supply pipe can be lower than the temperature of water supply and return water at the indoor heat dissipation tail end of a heat user, and the mutual influence on the hot water flow distribution of other heat users can be avoided in operation; and the heat exchange device can disperse cooling according to the needs of heat users in summer and can realize large-temperature-difference central heat supply for the primary and secondary heat supply networks in cities in winter.

In order to overcome the problems of the prior art, the technical scheme for solving the technical problems is as follows:

The utility model provides a user heat transfer device, includes delivery pipe (4), distribution delivery pipe (6), distribution wet return (7), characterized by: the user heat exchange device also comprises a water source heat pump (9); the water source heat pump (9) comprises four parts, namely a compressor (12), an evaporator (10), a condenser (11) and a throttle valve (13); the outlet end of the compressor (12) is connected with the inlet end of the compressor (12) in sequence through the inlet end of the condenser (11) on the refrigerant side, the outlet end of the condenser (11) on the refrigerant side, the throttle valve (13), the inlet end of the evaporator (10) on the refrigerant side and the outlet end of the evaporator (10) on the refrigerant side, so as to form a water source heat pump (9) refrigerant circulation system; the water side inlet end of the evaporator (10) is connected with the water supply pipe (4) through the outlet end of the distribution water supply pipe (6) and the inlet end of the distribution water supply pipe (6) in sequence; the water side outlet end of the evaporator (10) is connected with the water supply pipe (4) through the inlet end of the distribution return pipe (7) and the outlet end of the distribution return pipe (7) in sequence.

The following modifications are also possible for the above-described scheme.

1) The first improvement scheme is as follows: a preheater (19) is arranged on the distribution water supply pipe (6) between the water side inlet end of the evaporator (10) and the inlet end of the distribution water supply pipe (6); the inlet end of the high-temperature side of the preheater (19) is connected with the water supply pipe (4) through the inlet end of the distribution water supply pipe (6), and the outlet end of the high-temperature side of the preheater (19) is connected with the inlet end of the water side of the evaporator (10); the low-temperature side outlet end of the preheater (19) is connected with the water side inlet end of the condenser (11).

2) The second improvement scheme is as follows: the bypass inlet of the confluence three-way flow regulating valve (17) is connected with a distribution return pipe (7) between the water side outlet end of the evaporator (10) and the outlet end of the distribution return pipe (7) sequentially through the outlet end of a bypass pipe (23) and the inlet end of the bypass pipe (23); the outlet of the converging three-way flow regulating valve (17) is connected with the water side inlet end of the evaporator (10) through the outlet end of the distribution water supply pipe (6); the direct-current inlet of the converging three-way flow regulating valve (17) is connected with the water supply pipe (4) through the inlet end of the distribution water supply pipe (6).

3) The improvement scheme III: the direct current inlet of the confluence three-way flow regulating valve (17) sequentially passes through the outlet end of a bypass pipe (23) and the inlet end of the bypass pipe (23) and is connected with a distribution return pipe (7) between the water side outlet end of the evaporator (10) and the outlet end of the distribution return pipe (7); the outlet of the converging three-way flow regulating valve (17) is connected with the water side inlet end of the evaporator (10) through the outlet end of the distribution water supply pipe (6); the side inflow port of the converging three-way flow regulating valve (17) is connected with the water supply pipe (4) through the inlet end of the distribution water supply pipe (6).

4) The improvement scheme is as follows: the bypass outlet of the bypass three-way flow regulating valve (18) is connected with a distribution water supply pipe (6) between the water side inlet end of the evaporator (10) and the inlet end of the distribution water supply pipe (6) sequentially through the inlet end of a bypass pipe (23) and the outlet end of the bypass pipe (23); the inlet of the split three-way flow regulating valve (18) is connected with the water side outlet end of the evaporator (10) through the inlet end of the distribution return pipe (7); the straight outflow port of the split three-way flow regulating valve (18) is connected with the water supply pipe (4) through the outlet end of the distribution return pipe (7).

5) The improvement scheme is as follows: the straight outflow port of the split three-way flow regulating valve (18) is connected with a distribution water supply pipe (6) between the water side inlet end of the evaporator (10) and the inlet end of the distribution water supply pipe (6) sequentially through the inlet end of a bypass pipe (23) and the outlet end of the bypass pipe (23); the inlet of the split three-way flow regulating valve (18) is connected with the water side outlet end of the evaporator (10) through the inlet end of the distribution return pipe (7); the bypass outlet of the split three-way flow regulating valve (18) is connected with the water supply pipe (4) through the outlet end of the distribution return pipe (7).

6) The improvement scheme is six: a resistance valve (16) is arranged on the water supply pipe (4) between the inlet end of the distribution water supply pipe (6) and the outlet end of the distribution water return pipe (7).

The following further improvements are provided for the above-mentioned improvement:

A resistance valve (16) is arranged on the water supply pipe (4) between the inlet end of the distribution water supply pipe (6) and the outlet end of the distribution water return pipe (7).

Likewise, the following further improvements are also provided for the above-described second improvement:

A preheater (19) is arranged on the distribution water supply pipe (6) between the direct-current inlet of the converging three-way flow regulating valve (17) and the inlet end of the distribution water supply pipe (6); the inlet end of the high-temperature side of the preheater (19) is connected with the water supply pipe (4) through the inlet end of the distribution water supply pipe (6), and the outlet end of the high-temperature side of the preheater (19) is connected with the direct-current inlet of the converging three-way flow regulating valve (17); the low-temperature side outlet end of the preheater (19) is connected with the water side inlet end of the condenser (11).

The third improvement also has the following further improvements:

A preheater (19) is arranged on the distribution water supply pipe (6) between the side inflow port of the converging three-way flow regulating valve (17) and the inlet end of the distribution water supply pipe (6); the inlet end of the high-temperature side of the preheater (19) is connected with the water supply pipe (4) through the inlet end of the distribution water supply pipe (6), and the outlet end of the high-temperature side of the preheater (19) is connected with the side inflow port of the converging three-way flow regulating valve (17); the low-temperature side outlet end of the preheater (19) is connected with the water side inlet end of the condenser (11).

The following further improvements are also available for the above-described improvements four and five:

A preheater (19) is arranged on the distribution water supply pipe (6) between the outlet end of the bypass pipe (23) and the inlet end of the distribution water supply pipe (6); the inlet end of the high-temperature side of the preheater (19) is connected with the water supply pipe (4) through the inlet end of the distribution water supply pipe (6), and the outlet end of the high-temperature side of the preheater (19) is connected with the outlet end of the bypass pipe (23); the low-temperature side outlet end of the preheater (19) is connected with the water side inlet end of the condenser (11).

Compared with the prior art, the utility model has the beneficial effects that:

1. the number of the outdoor heat supply pipelines from the heat source to the heat user can be reduced, and the initial investment of an outdoor pipe network is reduced;

2. The hydraulic imbalance of the double-pipe hot water heating system can be overcome, and the mutual influence of water flow distribution of heat users is avoided;

3. The water supply and return temperatures of the heat user can be higher than the temperature of hot water in an outdoor water supply pipe, and the recycling of low-temperature waste heat with lower temperature is facilitated;

4. In summer, according to the needs of users, the distributed cooling with the users as units is realized, the energy is saved, and the running cost is lower; the urban primary and secondary heat supply networks can realize large-temperature-difference central heat supply simultaneously in winter;

5. The utility model is suitable for industrial and civil large-temperature-difference heat supply systems, and is especially suitable for occasions of waste heat recovery and renewable energy source heat supply.

Drawings

FIG. 1 is a schematic view of the structure of embodiment 1 of the present utility model;

FIG. 2 is a schematic structural view of embodiment 2 of the present utility model;

FIG. 3 is a schematic view of the structure of embodiment 3 of the present utility model;

FIG. 4 is a schematic view of the structure of embodiment 4 of the present utility model;

FIG. 5 is a schematic view of the structure of embodiment 5 of the present utility model;

FIG. 6 is a schematic view of the structure of embodiment 6 of the present utility model;

FIG. 7 is a schematic view of the structure of embodiment 7 of the present utility model;

FIG. 8 is a prior art schematic diagram;

fig. 9 is a schematic diagram of a prior art structure.

Detailed Description

The present utility model will be described in further detail with reference to the accompanying drawings.

Example 1

As shown in fig. 1, the present embodiment is a large temperature difference heating system using the present utility model, which is used in the occasions where there is a heating demand. The whole system comprises the following components: the heat source station 1, the circulating pump 2, the water supply pipe 4, the backwater temperature sensor 22 and 4 heat users 3 (shown as a diagram a, a diagram b, a diagram c and a diagram d in fig. 1). Wherein the user introduction port of the heat user 3 shown in fig. 1c and d uses the user heat exchange device 50 according to the present utility model.

The user heat exchange device 50 of the heat user 3 shown in the diagram c in fig. 1 consists of the following parts: a water supply pipe 4, a distribution water supply pipe 6, a distribution return pipe 7, a distribution water pump 5, a water source heat pump 9 and an indoor water pump 21.

The user heat exchange device 50 of the heat user 3 shown in the diagram d in fig. 1 consists of the following parts: a water supply pipe 4, a distribution water supply pipe 6, a distribution return pipe 7, a resistance valve 16, a water source heat pump 9 and an indoor water pump 21.

As shown in fig. 1, the water source heat pump 9 basically comprises: an evaporator 10, a condenser 11, a compressor 12, and a throttle valve 13. The connection mode is as follows: the outlet end of the compressor 12 is connected with the inlet end of the compressor 12 through the inlet end of the condenser 11 on the refrigerant side, the outlet end of the condenser 11 on the refrigerant side, the throttle valve 13, the inlet end of the evaporator 10 on the refrigerant side and the outlet end of the evaporator 10 on the refrigerant side in sequence; a refrigerant circulation system of the water source heat pump 9 is constituted.

The heat user 3 and the water supply pipe 4 shown in the figure a and the figure b in figure 1 are directly connected; because the temperature of the hot water in the water supply pipe 4 can just meet the needs of the indoor heat radiation ends 20 of the two heat users 3, the hot water in the water supply pipe 4 directly enters the indoor heat radiation ends 20 to heat the users.

The heat user 3 and the water supply pipe 4 shown in the diagrams c and d in fig. 1 are indirectly connected; since the temperature of the hot water in the water supply pipe 4 is lower than the temperature of the hot water required at the inlet end of the indoor heat radiation ends 20 of the two heat consumers 3, the indoor heat radiation ends 20 cannot be satisfied, and therefore, the water source heat pump 9 is arranged in the consumer heat exchanging device 50 of the two heat consumers 3 for extracting heat from the hot water in the water supply pipe 4 to heat the heat consumers 3 shown in the figures c and d.

For the heat users 3 shown in fig. 1 c and d, the indoor heat radiation end 20, the indoor water pump 21, the indoor water return pipe 25, the condenser 11 of the water source heat pump 9 and the indoor water supply pipe 24 are connected in sequence to form an indoor system of the two heat users 3. The indoor system is connected in the following way: the water side outlet end of the condenser 11 is connected with the inlet end of the indoor heat dissipation end 20 through an indoor water supply pipe 24, and the outlet end of the indoor heat dissipation end 20 is connected with the water side inlet end of the condenser 11 through an indoor water pump 21 suction end, an indoor water pump 21 extrusion end and an indoor water return pipe 25 in sequence. In practice, for the above-described indoor system, the indoor water pump 21 may also be installed on the indoor water supply pipe 24 between the water side outlet end of the condenser 11 and the inlet end of the indoor heat radiation end 20. The above-described installation of the indoor water pump 21 is applicable to the solutions described in all embodiments of the present utility model. When the indoor heat-dissipating device works, the evaporator 10 of the water source heat pump 9 extracts heat from hot water of the water supply pipe 4, and then the condenser 11 of the water source heat pump 9 heats low-temperature hot water from the outlet end of the indoor heat-dissipating end 20, so that the low-temperature hot water is heated to meet the water temperature requirement of the inlet end of the indoor heat-dissipating end 20, and then the low-temperature hot water is supplied to the indoor heat-dissipating end 20 for heating of a heat user.

As shown in fig. 1, the resistance valve 16 is a control valve capable of regulating the pressure difference, such as: a differential pressure control valve. For the heat consumer 3 shown in fig. 1 a, the resistance valve 16 is operative to control the pressure difference between the distribution water supply pipe 6 and the distribution return pipe 7 to a given desired value for regulating the flow of hot water into the indoor heat dissipating end 20.

For the heat consumer 3 shown in fig. 1, d, the function of the resistance valve 16 is to control the pressure difference between the water side inlet end of the evaporator 10 and the water side outlet end of the evaporator 10 to a given desired value, so that the flow of hot water into the evaporator 10 is at the given desired value.

The heat source station 1 can be any one or more of a boiler, a heat pump unit (especially a transcritical carbon dioxide air source heat pump), a waste heat recovery device, an urban heat supply network heat exchange station, a geothermal well heat exchange station, a heat accumulator and the like.

The heat consumer 3 is a heating system of one building, or a heating system of a different area of one building, for example: a high-rise building high-district heating system and a low-district heating system.

The indoor heat dissipating end 20 in the heat consumer 3 may be any of a radiator, a floor heater, a fan coil, or the like. Each set of indoor heat dissipating ends 20 is provided with a temperature controlled valve for controlling room temperature.

The distribution water pump 5 is a variable frequency pump. For the heat consumer 3 shown in fig. 1 b, the function of the distribution water pump 5 is to control the pressure difference between the inlet end and the outlet end of the indoor heat radiation end 20 to a given desired value, so as to regulate the flow of hot water entering the indoor heat radiation end 20.

For the heat consumer 3 shown in fig. 1c, the function of the distribution water pump 5 in the consumer heat exchange device 50 is to control the pressure difference between the water side inlet end of the evaporator 10 and the water side outlet end of the evaporator 10 to a given desired value, so that the flow of hot water into the evaporator 10 is at the given desired value. Because in practical application, in order to ensure that the water source heat pump 9 in the user heat exchange device 50 works normally, there is generally a minimum flow requirement for the flow of hot water through the evaporator 10 thereof, and in order to ensure efficient operation of the water source heat pump 9, a manufacturer will normally give a recommended flow of hot water, so that the flow of hot water through the evaporator 10 should be kept stable during operation and within the recommended flow range of hot water; because the flow of hot water into the evaporator 10 is often not good beyond the manufacturer's recommended flow of hot water, it can cause a transition flushing of the heat exchange tube bundles by the water flow in the evaporator 10, affecting the service life of the unit. The above-described method of controlling the flow of hot water into the evaporator 10 to a given desired value is applicable to all user heat exchange device 50 arrangements of the present utility model in which the distribution water pump 5 is a variable frequency pump.

In operation, the working flow of the large temperature difference heating system using the present utility model shown in fig. 1 is as follows, and the working flow of the user heat exchange device 50 of the present utility model can be seen from the working process of the heat user 3 shown in fig. c and d:

In operation, hot water heated by the heat source station 1 sequentially enters the water supply pipe 4 through the outlet end A of the heat source station 1 and the inlet end of the water supply pipe 4, flows to the heat user 3 shown in the figure a in fig. 1 through the water supply pipe 4, and is divided into two paths; the first hot water sequentially passes through the inlet end of the resistance valve 16 and the outlet end of the resistance valve 16 and flows into the water supply pipe 4 at the outlet end of the resistance valve 16; the second hot water sequentially passes through the inlet end of the distribution water supply pipe 6, the outlet end of the distribution water supply pipe 6 and the inlet end of the indoor heat dissipation tail end 20, and enters the indoor heat dissipation tail end 20 to heat a user; after the temperature of the hot water is reduced, the hot water sequentially passes through the outlet end of the indoor heat dissipation tail end 20, the inlet end of the distribution return pipe 7 and the outlet end of the distribution return pipe 7 and flows into the water supply pipe 4 at the outlet end of the resistance valve 16;

After being mixed in the water supply pipe 4 at the outlet end of the resistance valve 16, the two paths of hot water flow to the heat user 3 shown in the diagram b in fig. 1 along the water supply pipe 4 and are divided into two paths; the first hot water sequentially passes through the connection point of the inlet end of the distribution water supply pipe 6 and the water supply pipe 4, the connection point of the outlet end of the distribution water return pipe 7 and the water supply pipe 4, and enters the water supply pipe 4 at the downstream of the connection point of the outlet end of the distribution water return pipe 7 and the water supply pipe 4; the second hot water sequentially passes through the inlet end of the distribution water supply pipe 6, the suction end of the distribution water pump 5, the extrusion end of the distribution water pump 5, the outlet end of the distribution water supply pipe 6 and the inlet end of the indoor heat dissipation end 20, and enters the indoor heat dissipation end 20 to heat a user; after the temperature of the hot water is reduced, the hot water sequentially passes through the outlet end of the indoor heat dissipation end 20, the inlet end of the distribution return pipe 7 and the outlet end of the distribution return pipe 7 and also flows into the water supply pipe 4 at the downstream of the connection point of the outlet end of the distribution return pipe 7 and the water supply pipe 4;

After being mixed in the water supply pipe 4, the two paths of hot water flow into the user heat exchange device 50 of the heat user 3 shown in the diagram c in fig. 1 along the water supply pipe 4 and are divided into two paths; the first hot water sequentially passes through the connection point of the inlet end of the distribution water supply pipe 6 and the water supply pipe 4, the connection point of the outlet end of the distribution water return pipe 7 and the water supply pipe 4, and enters the water supply pipe 4 at the downstream of the connection point of the outlet end of the distribution water return pipe 7 and the water supply pipe 4; the second hot water sequentially passes through the inlet end of the distribution water supply pipe 6, the suction end of the distribution water pump 5, the extrusion end of the distribution water pump 5, the outlet end of the distribution water supply pipe 6 and the water side inlet end of the evaporator 10, and enters the evaporator 10 to perform indirect heat exchange with the refrigerant; after the heat released by the hot water and the water temperature are reduced, the hot water sequentially passes through the water side outlet end of the evaporator 10, the inlet end of the distribution return pipe 7 and the outlet end of the distribution return pipe 7 and also flows into the water supply pipe 4 at the downstream of the connection point of the outlet end of the distribution return pipe 7 and the water supply pipe 4;

The two paths of hot water are mixed in the water supply pipe 4, come out of the user heat exchange device 50 of the heat user 3 shown in the graph c in fig. 1, flow into the user heat exchange device 50 of the heat user 3 shown in the graph d in fig. 1 along the water supply pipe 4, and are divided into two paths; the first hot water sequentially passes through the inlet end of the resistance valve 16 and the outlet end of the resistance valve 16 and flows into the water supply pipe 4 at the outlet end of the resistance valve 16; the second hot water sequentially passes through the inlet end of the distribution water supply pipe 6, the outlet end of the distribution water supply pipe 6 and the water side inlet end of the evaporator 10, and enters the evaporator 10 to perform indirect heat exchange with the refrigerant; after the heat released by the hot water and the water temperature are reduced, the hot water sequentially passes through the water side outlet end of the evaporator 10, the inlet end of the distribution return pipe 7 and the outlet end of the distribution return pipe 7 and flows into the water supply pipe 4 at the outlet end of the resistance valve 16;

The two paths of hot water are mixed in the water supply pipe 4 at the outlet end of the resistance valve 16, come out of the user heat exchange device 50 of the heat user 3 shown in the graph d in fig. 1, sequentially pass through the suction end of the circulating pump 2, the extrusion end of the circulating pump 2, the outlet end of the water supply pipe 4 and the inlet end B of the heat source station 1, return to the heat source station 1 to be heated again, and sequentially enter the water supply pipe 4 through the outlet end A of the heat source station 1 and the inlet end of the water supply pipe 4; the working cycle of the large-temperature-difference heating system using the utility model shown in fig. 1 is completed once.

In the working cycle process of the large-temperature difference heating system using the utility model, for the schemes shown in the figures c and d, the working flow of the refrigerant of the water source heat pump 9 in the user heat exchange device 50 is as follows:

In operation, in the evaporator 10, the gas-liquid two-phase mixture of the low temperature and low pressure refrigerant is indirectly heat exchanged with the hot water from the hot water pipe 4, the refrigerant absorbs the heat of the hot water and is gasified into low temperature and low pressure refrigerant gas, the low temperature and low pressure refrigerant gas enters the compressor 12 to be compressed into high temperature and high pressure refrigerant superheated gas, the refrigerant superheated gas enters the condenser 11 to heat the indoor system backwater, the temperature of the refrigerant superheated gas reaches the requirement of water supply temperature, and the refrigerant gas is sent to the indoor heat dissipation terminal 20 to heat a user; in the condenser 11, the superheated refrigerant gas is condensed into a liquid after giving off heat, and then enters the throttle valve 13, throttled into a low-temperature low-pressure refrigerant gas-liquid two-phase mixture, and then enters the evaporator 10, thus completing one refrigerant heat pump cycle.

In the working cycle process of the large-temperature-difference heating system using the utility model, the hot water in the water supply pipe 4 sequentially emits heat to the heat user 3 shown in the diagram a, the diagram b, the diagram c and the diagram d in fig. 1, the temperature of the hot water in the water supply pipe 4 is sequentially reduced, and then the flow rate of the hot water in the water supply pipe 4 is controlled by the circulating pump 2, so that the large-temperature-difference operation can be realized.

In the working cycle process of the large-temperature-difference heating system using the utility model, for the schemes shown in the figure c and the figure d, the water source heat pump 9 in the user heat exchange device 50 extracts heat from hot water of the water supply pipe 4 through the evaporator 10, heats indoor system backwater through the condenser 11 to enable the temperature to reach the requirement of water supply temperature, and then sends the backwater to the indoor heat dissipation tail end 20 to heat the user; thus, the water supply and return temperatures of the indoor system can be made higher than the hot water temperature in the water supply pipe 4.

During the working cycle of the large-temperature difference heating system using the utility model, the flow rate of the hot water in the upstream water supply pipe 4 of each heat user 3 (namely, the flow rate of the hot water in the upstream water supply pipe 4 of the connection point of the inlet end of the distribution water supply pipe 6 and the water supply pipe 4) is equal to the flow rate of the hot water in the downstream water supply pipe 4 of the heat user 3 (namely, the flow rate of the hot water in the downstream water supply pipe 4 of the connection point of the outlet end of the distribution water return pipe 7 and the water supply pipe 4); therefore, the hydraulic imbalance existing in the double-pipe hot water heating system can be overcome, and the mutual influence of hot water flow distribution of each heat user 3 is avoided.

The control method of the large-temperature-difference heating system using the utility model in working shown in figure 1 is as follows:

1) When the heat source station 1 is any one of a boiler, a heat pump unit, a waste heat recovery device, an urban heat supply network heat exchange station, a geothermal well heat exchange station, a heat accumulator and the like, which can regulate and control the hot water outlet temperature of the heat source station 1, the hot water outlet temperature of the heat source station 1 is regulated and controlled according to the outdoor air temperature by a climate compensation curve set in a controller of the heat source station 1 (namely: the hot water outlet temperature of the outlet end A of the heat source station 1);

2) As shown in fig. 1, a return water temperature sensor 22 is provided on the pipe at the outlet end of the water supply pipe 4 for detecting the actual hot water temperature at the outlet end of the water supply pipe 4. In the working process, when the circulating pump 2 is a variable frequency pump, the actual hot water temperature at the outlet end of the water supply pipe 4 detected by the backwater temperature sensor 22 is transmitted to the controller of the heat source station 1 and is compared with the hot water temperature expected value at the outlet end of the water supply pipe 4 set by the controller; according to the comparison result, the flow rate of the hot water in the water supply pipe 4 is regulated by changing the operation frequency of the circulation pump 2, so that the actual hot water temperature at the outlet end of the water supply pipe 4 is within a desired range.

In the user heat exchange device 50 of the heat user 3 shown in the diagram c in fig. 1, the distribution water pump 5 is provided on the distribution water supply pipe 6, but in actual application, the distribution water pump 5 may be provided on the distribution water return pipe 7.

Example 2

As shown in fig. 2, the present embodiment is also a large temperature difference heating system using the present utility model, which is used in the occasions with heating requirements; the system shown in fig. 2 has two heat users 3 in common, namely: the hot user 3 shown in figures a, b of figure 2; the user inlets of both heat users 3 use the user heat exchange device 50 according to the utility model.

The difference between the user heat exchange device 50 in the heat consumer 3 shown in fig. 2 a and the user heat exchange device 50 in the heat consumer 3 shown in fig. 1 d is that: a preheater 19 is provided on the distribution water supply line 6 of the consumer heat exchange device 50.

The difference between the user heat exchange device 50 in the heat consumer 3 shown in fig. 2 b and the user heat exchange device 50 in the heat consumer 3 shown in fig. 1 c is that: 1) A preheater 19 is provided on the distribution water supply line 6 of the consumer heat exchange device 50; 2) The distributing water pump 5 in the user heat exchange device 50 is arranged on the distributing water return pipe 7.

In operation, in the user heat exchange device 50, the preheater 19 functions as: the hot water in the upstream water supply pipe 4 is utilized to preheat the indoor system backwater so as to reduce the operation energy consumption of the water source heat pump 9.

In practical application, the circulating pump 2 is a variable frequency pump. In the user heat exchange device 50, the function of the resistance valve 16 in the heat user 3 shown in fig. 2a is the same as in the heat user 3 shown in fig. 1 d. In the user heat exchange device 50, the function of the distribution water pump 5 in the heat user 3 shown in the diagram b in fig. 2 is the same as that in the heat user 3 shown in the diagram c in fig. 1.

As shown in fig. 2, the basic composition and refrigerant workflow of the water source heat pump 9 in the user heat exchange device 50 are also the same as those of the scheme shown in fig. 1.

In operation, the working process of the large temperature difference heating system shown in fig. 2 is divided into the following two cases, and the following description is given respectively; the working process of the user heat exchange device 50 according to the utility model can also be seen from the working process of the heat user 3 shown in figures a, b.

(1) When the flow rate of hot water in the hot water pipe 4 is greater than the flow rate of hot water required by the evaporators 10 of the two heat consumers 3 in the system of fig. 2, the working flow of the large-temperature difference heating system of fig. 2 using the present utility model is as follows:

In operation, hot water heated by the heat source station 1 sequentially enters the water supply pipe 4 through the outlet end A of the heat source station 1 and the inlet end of the water supply pipe 4, flows into the user heat exchange device 50 of the heat user 3 shown in the diagram a in fig. 2 through the water supply pipe 4, and is divided into two paths; the first hot water sequentially passes through the inlet end of the resistance valve 16 and the outlet end of the resistance valve 16 and flows into the water supply pipe 4 at the outlet end of the resistance valve 16; the second hot water sequentially passes through the inlet end of the distribution water supply pipe 6 and the high-temperature side inlet end of the preheater 19, enters the preheater 19, and performs indirect heat exchange with indoor system backwater to preheat backwater; after the heat released by the hot water and the water temperature are reduced, the hot water sequentially passes through the outlet end of the high temperature side of the preheater 19, the outlet end of the distribution water supply pipe 6 and the inlet end of the water side of the evaporator 10, and enters the evaporator 10 to perform indirect heat exchange with the refrigerant; after the heat is released again and the water temperature is reduced again, the hot water sequentially passes through the water side outlet end of the evaporator 10, the inlet end of the distribution return pipe 7 and the outlet end of the distribution return pipe 7 and flows into the water supply pipe 4 at the outlet end of the resistance valve 16;

The two paths of hot water are mixed in the water supply pipe 4, and after coming out of the user heat exchange device 50 of the heat user 3 shown in the diagram a in fig. 2, the hot water flows into the user heat exchange device 50 of the heat user 3 shown in the diagram b in fig. 2 along the water supply pipe 4 and is divided into two paths; the first hot water sequentially passes through the connection point of the inlet end of the distribution water supply pipe 6 and the water supply pipe 4, the connection point of the outlet end of the distribution water return pipe 7 and the water supply pipe 4, and enters the water supply pipe 4 at the downstream of the connection point of the outlet end of the distribution water return pipe 7 and the water supply pipe 4; the second hot water sequentially passes through the inlet end of the distribution water supply pipe 6 and the high-temperature side inlet end of the preheater 19, enters the preheater 19, and performs indirect heat exchange with indoor system backwater to preheat backwater; after the heat released by the hot water and the water temperature are reduced, the hot water sequentially passes through the outlet end of the high temperature side of the preheater 19, the outlet end of the distribution water supply pipe 6 and the inlet end of the water side of the evaporator 10, and enters the evaporator 10 to perform indirect heat exchange with the refrigerant; the hot water emits heat again, the water temperature is reduced again, and then the hot water sequentially passes through the water side outlet end of the evaporator 10, the inlet end of the distribution return pipe 7, the suction end of the distribution water pump 5, the extrusion end of the distribution water pump 5 and the outlet end of the distribution return pipe 7, and flows into the water supply pipe 4 at the downstream of the connection point of the outlet end of the distribution return pipe 7 and the water supply pipe 4;

the two paths of hot water are mixed in the water supply pipe 4, come out of the user heat exchange device 50 of the heat user 3 shown in the diagram B in fig. 2, sequentially pass through the suction end of the circulating pump 2, the extrusion end of the circulating pump 2, the outlet end of the water supply pipe 4 and the inlet end B of the heat source station 1, return to the heat source station 1 to be heated again, and sequentially enter the water supply pipe 4 through the outlet end A of the heat source station 1 and the inlet end of the water supply pipe 4; the working cycle of the large temperature difference heating system using the utility model shown in fig. 2 is completed once.

(2) In operation, when the flow of hot water in the hot water pipe 4 is less than the flow of hot water required by the evaporator 10 of the heat consumer 3 shown in fig. 2 b, the flow of operation of the large temperature difference heating system of fig. 2 using the present utility model is as follows:

The two paths of hot water are mixed in the water supply pipe 4, and after coming out of the user heat exchange device 50 of the heat user 3 shown in the diagram a in fig. 2, the hot water flows to the heat user 3 shown in the diagram b in fig. 2 along the water supply pipe 4 and enters the inlet end of the distribution water supply pipe 6 in the user heat exchange device 50 of the heat user 3; mixing with a part of hot water returned from the outlet end of the distribution return pipe 7 of the user heat exchange device 50 to the inlet end of the distribution water supply pipe 6; then sequentially passes through the inlet end of the distribution water supply pipe 6 of the user heat exchange device 50 and the high-temperature side inlet end of the preheater 19, enters the preheater 19, and performs indirect heat exchange with indoor system backwater to preheat backwater; after the heat released by the hot water and the water temperature are reduced, the hot water sequentially passes through the outlet end of the high temperature side of the preheater 19, the outlet end of the distribution water supply pipe 6 and the inlet end of the water side of the evaporator 10, and enters the evaporator 10 to perform indirect heat exchange with the refrigerant; the hot water emits heat again, the water temperature is reduced again, and then the hot water sequentially passes through the water side outlet end of the evaporator 10, the inlet end of the distribution return pipe 7, the suction end of the distribution water pump 5, the extrusion end of the distribution water pump 5 and the outlet end of the distribution return pipe 7, and is divided into two paths; the first hot water is returned to the inlet end of the distribution water supply pipe 6 of the user heat exchange device 50 along the water supply pipe 4; the second hot water flows into the water supply pipe 4 at the downstream of the user heat exchange device 50, sequentially passes through the suction end of the circulating pump 2, the extrusion end of the circulating pump 2, the outlet end of the water supply pipe 4 and the inlet end B of the heat source station 1, returns to the heat source station 1 to be heated again, and sequentially passes through the outlet end A of the heat source station 1 and the inlet end of the water supply pipe 4 to enter the water supply pipe 4; the working cycle of the large temperature difference heating system using the utility model shown in fig. 2 is completed once.

In the working cycle process of the large-temperature-difference heat supply system, the working flow of the indoor system of the heat user 3 shown in the diagram a and the diagram b in fig. 2 is the same, and the specific working process is as follows:

When the indoor heat dissipation device works, indoor system backwater from the outlet end of the indoor heat dissipation tail end 20 sequentially passes through the indoor backwater pipe 25 and the low-temperature side inlet end of the preheater 19, enters the preheater 19 and performs indirect heat exchange with hot water with higher temperature from the water supply pipe 4; after the absorbed heat is preheated, the preheated heat sequentially passes through a low-temperature side outlet end of the preheater 19, an intake end of the indoor water pump 21, an extrusion end of the indoor water pump 21 and a water side inlet end of the condenser 11, enters the condenser 11, and is subjected to indirect heat exchange with the refrigerant superheated gas from the compressor 12, the preheated indoor system backwater is heated again, and after the temperature reaches the indoor system water supply requirement, the preheated heat sequentially passes through the water side outlet end of the condenser 11, the indoor water supply pipe 24 and the indoor heat dissipation end 20 inlet end, and enters the indoor heat dissipation end 20 to supply heat for a user; after the temperature is reduced, the water returns to the low-temperature side inlet end of the preheater 19 through the outlet end of the indoor heat dissipation end 20, so that one indoor system hot water circulation is completed.

For the user heat exchange device 50 in the heat user 3 shown in the diagram b in fig. 2, the distribution water pump 5 thereof may also be provided at the distribution water supply pipe 6 between the water side inlet end of the evaporator 10 and the high temperature side outlet end of the preheater 19; the distribution water pump 5 may also be provided on the distribution water supply pipe 6 at the high temperature side inlet end of the preheater 19. The method of setting the preheater 19 in the system according to this embodiment is applicable to all of the user heat exchange devices 50 of the present utility model.

For the user heat exchange device 50 in the heat user 3 shown in fig. 1 c, when the flow rate of the hot water in the upstream water supply pipe 4 is smaller than the required flow rate of the hot water required by the evaporator 10 of the user heat exchange device 50 during the operation, a part of the hot water will also return to the inlet end of the distribution water supply pipe 6 of the user heat exchange device 50 from the outlet end of the distribution water return pipe 7 of the user heat exchange device 50 through the water supply pipe 4, and then pass through the inlet end of the distribution water supply pipe 6 of the user heat exchange device 50, the suction end of the distribution water pump 5, the extrusion end of the distribution water pump 5, the outlet end of the distribution water supply pipe 6, the water side inlet end of the evaporator 10 in sequence after being mixed with the hot water from the upstream water supply pipe 4, and enter the evaporator 10.

Example 3

As shown in fig. 3, this embodiment is also a large temperature difference heating system using the present utility model, which is used in the occasions where there is a heating demand. The heat source station 1 in this embodiment is an urban heat network heat exchange station comprising: city heat supply pipe 101, city heat supply pipe 100, plate heat exchanger 55, electric regulating valve 32. In operation, the electric control valve 32 regulates and controls the temperature of the hot water at the outlet end of the low temperature side of the plate heat exchanger 55 (i.e., the hot water outlet temperature at the outlet end A of the heat source station 1) by regulating and controlling the flow of primary network hot water entering the plate heat exchanger 55 through the urban heat network water supply pipe 101 according to the climate compensation curve set in the controller of the heat source station 1 and according to the outdoor air temperature.

The system shown in fig. 3 has two heat users 3 in common, namely: the hot user 3 shown in figures a, b of figure 3; the user inlet of the heat consumer 3 shown in figure b uses the consumer heat exchange device 50 according to the utility model.

The heat consumer 3 shown in fig. 3a is indirectly connected to the water supply line 4 via a water-water heat exchanger 28. The resistance valve 16 is an electric control valve for controlling the water supply temperature of the indoor system, namely: the hot water temperature at the low temperature side outlet end of the water-water type heat exchanger 28 of the heat consumer 3.

The user heat exchange device 50 of the heat user 3 shown in fig. 3 b differs from the user heat exchange device 50 of the heat user 3 shown in fig. 1 c in that: 1) A diversion three-way flow regulating valve 18 is arranged on the distribution return pipe 7 of the user heat exchange device 50; 2) In the user heat exchange device 50, the distribution water pump 5 is arranged on a pipeline between the water side outlet end of the evaporator 10 and the inlet of the diversion three-way flow regulating valve 18.

Because in actual engineering, for the water source heat pump 9 in the user heat exchange device 50, the evaporator 10 of some models of water source heat pump 9 has the highest water temperature limit value in addition to the lowest water flow limit value requirement, and the water temperature entering the evaporator 10; beyond the maximum water temperature limit, the water source heat pump 9 cannot work normally; in operation, therefore, the split three-way flow regulating valve 18 functions in the user heat exchange device 50 of the heat user 3 shown in fig. 3 b as: a part of low-temperature hot water coming out from the water side outlet end of the evaporator 10 of the user heat exchange device 50 sequentially passes through the inlet end of the distribution return pipe 7, the suction end of the distribution water pump 5, the extrusion end of the distribution water pump 5, the inlet of the distribution three-way flow regulating valve 18, the side outlet of the distribution three-way flow regulating valve 18, the inlet end of the bypass pipe 23 and the outlet end of the bypass pipe 23 of the user heat exchange device 50 and returns to the distribution water supply pipe 6 of the user heat exchange device 50; and the hot water is mixed with the hot water from the upstream water supply pipe 4 which passes through the inlet end of the distribution water supply pipe 6 of the user heat exchange device 50 and enters a part of the distribution water supply pipe 6, so that the temperature of the hot water at the water side inlet end of the evaporator 10 of the user heat exchange device 50 is regulated.

The function of the distribution water pump 5 in the user heat exchange device 50 shown in fig. 3 of the present embodiment is the same as that in the user heat exchange device 50 shown in fig. c of fig. 1; the basic composition of the water source heat pump 9 shown in fig. 3 and the refrigerant workflow are also the same as those of the water source heat pump 9 shown in fig. 1 c.

When in use, the circulating pump 2 is a variable frequency pump. The function of the booster pump 14 is: additional circulating power is provided to the system to make up for the shortfall of the circulating pump 2.

In operation, the working flow of the large temperature difference heating system using the present utility model shown in fig. 3 is as follows, and the working flow of the user heat exchange device 50 of the present utility model can be seen from the working flow of the heat user 3 shown in fig. b:

During operation, hot water heated by the heat source station 1 sequentially enters the water supply pipe 4 through the outlet end A of the heat source station 1 and the inlet end of the water supply pipe 4, flows to the heat user 3 shown in the figure a in figure 3 through the water supply pipe 4, and is divided into two paths; the first hot water sequentially passes through the inlet end of the resistance valve 16 and the outlet end of the resistance valve 16 and flows into the water supply pipe 4 at the outlet end of the resistance valve 16; the second hot water sequentially passes through the inlet end of the distribution water supply pipe 6, the outlet end of the distribution water supply pipe 6 and the high-temperature side inlet end of the water-water type heat exchanger 28 and enters the water-water type heat exchanger 28; indirect heat exchange is carried out on the indoor system backwater of the heat user 3, and the heat released by the hot water heats the indoor system backwater; after the water temperature is reduced, the water flows through the outlet end of the high temperature side of the water-water type heat exchanger 28, the inlet end of the distribution return pipe 7 and the outlet end of the distribution return pipe 7 in sequence, and also flows into the water supply pipe 4 at the outlet end of the resistance valve 16;

After being mixed in the water supply pipe 4, the two paths of hot water continue to flow downstream along the water supply pipe 4, are pressurized by the pressurizing pump 14, and flow into the user heat exchange device 50 of the heat user 3 shown in the diagram b in fig. 3, and are divided into two paths; the first hot water does not enter the evaporator 10 of the user heat exchange device 50 for heat dissipation, but sequentially passes through the connection point of the inlet end of the distribution water supply pipe 6 and the water supply pipe 4, the connection point of the outlet end of the distribution water return pipe 7 and the water supply pipe 4, and enters the water supply pipe 4 at the downstream of the user heat exchange device 50;

The second hot water enters the distribution water supply pipe 6 through the inlet end of the distribution water supply pipe 6, flows out of the bypass outlet of the diversion three-way flow regulating valve 18, sequentially passes through the inlet end of the bypass pipe 23 and the outlet end of the bypass pipe 23, and returns to the distribution water supply pipe 6 for mixing, so that the temperature of the hot water at the water side inlet end of the evaporator 10 of the user heat exchange device 50 is regulated; the mixed hot water sequentially passes through the outlet end of the distribution water supply pipe 6 and the water side inlet end of the evaporator 10, and enters the evaporator 10 to perform indirect heat exchange with the refrigerant; after the heat released by the hot water and the water temperature are reduced, the hot water sequentially passes through the water side outlet end of the evaporator 10, the inlet end of the distribution return pipe 7, the suction end of the distribution water pump 5, the extrusion end of the distribution water pump 5 and the inlet of the distribution three-way flow regulating valve 18; the hot water enters a split-flow three-way flow regulating valve 18 and is divided into two parts of low-temperature hot water;

A part of low-temperature water sequentially passes through a bypass outlet of the diversion three-way flow regulating valve 18, an inlet end of the bypass pipe 23 and an outlet end of the bypass pipe 23 and returns to the distribution water supply pipe 6; the other part of low-temperature water sequentially passes through the straight outflow port of the diversion three-way flow regulating valve 18 and the outlet end of the distribution return pipe 7 and also flows into the water supply pipe 4 at the downstream of the user heat exchange device 50; heat is dissipated from the evaporator 10 which does not enter the user heat exchange device 50, and the heat is mixed with the first hot water flowing into the downstream through the water supply pipe 4 between the inlet end of the distribution water supply pipe 6 and the outlet end of the distribution water return pipe 7 of the user heat exchange device 50;

The hot water is mixed and after exiting from the user heat exchange device 50 of the heat user 3 shown in the diagram b of fig. 3, the hot water continues to flow to the circulation pump 2 along the water supply pipe 4; after being pressurized by the circulating pump 2, the hot water sequentially passes through the outlet end of the water supply pipe 4 and the inlet end B of the heat source station 1, and returns to the heat source station 1 to be heated again, so that the working cycle of the large-temperature-difference heat supply system using the utility model shown in figure 3 is completed.

In the above-described working cycle of the large temperature difference heating system using the present utility model, the indoor system working flow of the heat user 3 shown in the graph a in fig. 3 is as follows: the indoor system backwater from the outlet end of the indoor heat dissipation end 20 sequentially passes through the indoor backwater pipe 25, the suction end of the indoor water pump 21, the extrusion end of the indoor water pump 21, the low-temperature side inlet end of the water-water type heat exchanger 28, and enters the water-water type heat exchanger 28 to be indirectly heat exchanged with the hot water from the water supply pipe 4, and the indoor system backwater absorbs heat and is heated; after the temperature rises to meet the requirement of the water supply temperature of the indoor system, the water passes through the low-temperature side outlet end of the water-water type heat exchanger 28, the indoor water supply pipe 24 and the inlet end of the indoor heat dissipation tail end 20 in sequence, enters the indoor heat dissipation tail end 20 to heat a user, gives off heat, and returns to the outlet end of the indoor heat dissipation tail end 20 after the water temperature is reduced, so that the hot water working cycle of the indoor system of the heat user 3 shown in the diagram a in fig. 3 is completed.

In the above-described working cycle of the large temperature difference heating system using the present utility model, the indoor system work flow of the heat user 3 shown in the graph b of fig. 3 is as follows: the indoor system backwater from the outlet end of the indoor heat dissipation end 20 sequentially passes through the indoor backwater pipe 25, the suction end of the indoor water pump 21, the extrusion end of the indoor water pump 21 and the water side inlet end of the condenser 11, enters the condenser 11, and is subjected to indirect heat exchange with the refrigerant superheated gas from the compressor 12, and after the indoor system backwater is heated and the temperature reaches the indoor system water supply requirement, the backwater sequentially passes through the water side outlet end of the condenser 11, the indoor water supply pipe 24 and the indoor heat dissipation end 20 inlet end and enters the indoor heat dissipation end 20 to heat a user; after the temperature is reduced, the water returns to the indoor water return pipe 25 through the outlet end of the indoor heat dissipation end 20, so that one indoor system hot water circulation is completed.

In practice, in the user heat exchange device 50 of the heat user 3 shown in the diagram b in fig. 3, the distribution water pump 5 may be disposed on the distribution water supply pipe 6 between the water side inlet end of the evaporator 10 and the outlet end of the bypass pipe 23 of the user heat exchange device 50, and the extrusion end of the distribution water pump 5 is connected to the water side inlet end of the evaporator 10.

It should be noted that the large temperature difference heating system of the present utility model is shown in fig. 3, and the heat source station 1 is a city heat network heat exchange station, so that the hot water system composed of the plate heat exchanger 55, the water supply pipe 4, the circulation pump 2, the resistance valve 16, and the heat consumer 3 shown in fig. 3 a and b belongs to the secondary network. The water heating system composed of city heat supply network heat source, city heat supply network water supply pipe 101, city heat supply network water return pipe 100, plate heat exchanger 55, electric regulating valve 32, etc. belongs to primary network.

As is apparent from the above analysis of embodiment 3, when the plate heat exchanger 55, the water supply pipe 4, the circulation pump 2, the resistance valve 16, and the secondary network composed of the heat consumer 3 shown in fig. a and b in fig. 3 realize the large temperature difference operation, the temperature of the hot water in the municipal heat supply pipe 100 can be reduced by the heat exchange of the plate heat exchanger 55, thereby increasing the temperature difference of the hot water between the municipal heat supply pipe 101 and the municipal heat supply pipe 100, and the primary network can also realize the large temperature difference heat supply.

The connection mode of the split three-way flow regulating valve 18 in the system is applicable to all the user heat exchange devices 50 of the utility model which simultaneously use the water source heat pump 9 and the distribution water pump 5.

Example 4

As shown in fig. 4, this embodiment is also a large temperature difference heating system using the present utility model, which is used in the occasions where there is a heating demand. The heat source station 1 in this embodiment is a municipal heat supply network water supply pipe 101, a municipal heat supply network return pipe 100.

The system as shown in fig. 4 has two heat users 3 in common, namely: the hot user 3 shown in figures a, b of figure 4; the user inlet of the heat consumer 3 shown in figure b uses the consumer heat exchange device 50 according to the utility model.

As shown in fig. 4, the control valve 8 is typically an electric two-way valve, and is provided on any water supply pipe 4 other than the water supply pipe 4 between the inlet end of the distribution water supply pipe 6 and the outlet end of the distribution return pipe 7 of the same heat consumer 3. In operation, the regulating valve 8 has the functions of: by changing the valve opening of the regulating valve 8, the flow rate of the hot water in the water supply pipe 4 is regulated, so that the actual hot water temperature at the outlet end of the water supply pipe 4 is within a desired range. The specific control method comprises the following steps: a backwater temperature sensor 22 is arranged on the pipeline at the outlet end of the water supply pipe 4 and is used for detecting the actual hot water temperature at the outlet end of the water supply pipe 4. In the working process, the actual hot water temperature at the outlet end of the water supply pipe 4 detected by the backwater temperature sensor 22 is transmitted to the controller of the heat source station 1 and is compared with the hot water temperature expected value at the outlet end of the water supply pipe 4 set by the controller; according to the comparison result, the controller of the heat source station 1 sends out a command to regulate the flow of hot water in the water supply pipe 4 by changing the valve opening of the regulating valve 8, so that the actual hot water temperature at the outlet end of the water supply pipe 4 is within a desired range.

In practical application, the following method for controlling the hot water outlet temperature of the heat source station 1 may be added to the above-described control method; namely: when the heat source station 1 is any one of a boiler, a heat pump unit, a waste heat recovery device, an urban heat network heat exchange station, a geothermal well heat exchange station, a heat accumulator and the like, which can regulate and control the hot water outlet temperature of the heat source station 1, the hot water outlet temperature of the heat source station 1 (namely, the hot water outlet temperature of the outlet end A of the heat source station 1) is regulated and controlled according to the outdoor air temperature through a climate compensation curve set in a controller of the heat source station 1.

In operation, the distribution water pump 5 in the heat user 3 shown in the graph a in fig. 4 regulates and controls the indoor system water supply temperature of the heat user 3 by changing the working frequency, namely: the water-water heat exchanger 28 low temperature side outlet water temperature.

The user heat exchange device 50 of the heat user 3 shown in fig. 4b differs from the user heat exchange device 50 of the heat user 3 shown in fig. 1 c in that: a converging three-way flow regulating valve 17 is additionally arranged on the distribution water supply pipe 6. The function of the converging-tee flow regulator 17 in the user heat exchange device 50 is the same as the function of the diverging-tee flow regulator 18 in the embodiment of fig. 3.

In operation, the working flow of the large temperature difference heating system using the present utility model shown in fig. 4 is as follows, and the working flow of the user heat exchange device 50 of the present utility model can be seen from the working flow of the heat user 3 shown in fig. b:

When in operation, under the action of the pressure difference between the urban heat supply network water supply pipe 101 and the urban heat supply network water return pipe 100, hot water from the urban heat supply network water supply pipe 101 sequentially enters the water supply pipe 4 through the outlet end A of the heat source station 1 and the inlet end of the water supply pipe 4, flows to the heat user 3 shown in the diagram a in fig. 4 through the water supply pipe 4, and is divided into two paths; the first hot water sequentially passes through the connection point of the inlet end of the distribution water supply pipe 6 and the water supply pipe 4, the connection point of the outlet end of the distribution water return pipe 7 and the water supply pipe 4, and enters the water supply pipe 4 at the downstream of the connection point of the outlet end of the distribution water return pipe 7 and the water supply pipe 4;

The second hot water sequentially passes through the inlet end of the distribution water supply pipe 6, the outlet end of the distribution water supply pipe 6 and the high-temperature side inlet end of the water-water type heat exchanger 28 and enters the water-water type heat exchanger 28; indirect heat exchange is carried out on the indoor system backwater of the heat user 3, and the heat released by the hot water heats the indoor system backwater; after the temperature of the hot water is reduced, the hot water sequentially passes through the outlet end of the high temperature side of the water-water type heat exchanger 28, the inlet end of the distribution return pipe 7, the suction end of the distribution water pump 5, the extrusion end of the distribution water pump 5 and the outlet end of the distribution return pipe 7, and also enters the downstream water supply pipe 4;

After being mixed in the water supply pipe 4, the two paths of hot water continue to flow downstream along the water supply pipe 4, flow into the user heat exchange device 50 of the heat user 3 shown in the diagram b in fig. 4 and are divided into two paths; the first hot water does not enter the evaporator 10 of the user heat exchange device 50 for heat dissipation, but sequentially passes through the connection point of the inlet end of the distribution water supply pipe 6 and the water supply pipe 4, the connection point of the outlet end of the distribution water return pipe 7 and the water supply pipe 4, and enters the water supply pipe 4 at the downstream of the user heat exchange device 50;

The second hot water sequentially passes through the inlet end of the distribution water supply pipe 6 and the direct-current inlet of the converging three-way flow regulating valve 17, enters the converging three-way flow regulating valve 17, is mixed with hot water from the distribution water return pipe 7 and also enters part of the converging three-way flow regulating valve 17 through the side inlet of the converging three-way flow regulating valve 17, so that the temperature of the hot water at the water side inlet end of the evaporator 10 of the user heat exchange device 50 is regulated;

The mixed hot water sequentially passes through the outlet of the converging three-way flow regulating valve 17, the suction end of the distribution water pump 5, the extrusion end of the distribution water pump 5, the outlet end of the distribution water supply pipe 6 and the water side inlet end of the evaporator 10, and enters the evaporator 10 to perform indirect heat exchange with the refrigerant; after the heat released by the hot water and the water temperature is reduced, the low-temperature hot water sequentially passes through the water side outlet end of the evaporator 10 and the inlet end of the distribution return pipe 7, and enters the distribution return pipe 7 to be divided into two parts of low-temperature hot water; a part of low-temperature water sequentially passes through the bypass pipe 23 and the side inflow port of the converging three-way flow regulating valve 17 and returns to the converging three-way flow regulating valve 17;

The other part of low-temperature water flows into the water supply pipe 4 at the downstream of the user heat exchange device 50 through the outlet end of the distribution return pipe 7; heat is dissipated from the evaporator 10 which does not enter the user heat exchange device 50, and flows into the first path of hot water downstream of the user heat exchange device 50 through the water supply pipe 4 between the inlet end of the distribution water supply pipe 6 and the outlet end of the distribution water return pipe 7 of the user heat exchange device 50;

The two paths of hot water are mixed and after exiting from the user heat exchange device 50 of the heat user 3 shown in the diagram b in fig. 4, the mixture continues to flow to the regulating valve 8 along the water supply pipe 4; and then sequentially passes through the regulating valve 8, the outlet end of the water supply pipe 4 and the inlet end B of the heat source station 1 and returns to the urban heat supply network water return pipe 100, thus completing the working cycle of the large-temperature-difference heat supply system using the utility model shown in figure 4.

In the above-described operation cycle of the large temperature difference heating system using the present utility model, the indoor system workflow of the heat user 3 shown in the diagram a in fig. 4 of the present embodiment is the same as the indoor system workflow of the heat user 3 shown in the diagram a in fig. 3.

In the above-described working cycle of the large temperature difference heating system using the present utility model, the indoor system workflow of the heat user 3 shown in the diagram b in fig. 4 is the same as the indoor system workflow of the heat user 3 shown in the diagram b in fig. 3;

Likewise, the refrigerant system operation of the user heat exchange device 50 in the scheme shown in fig. 4 of the present embodiment is the same as the refrigerant system operation of the user heat exchange device 50 in the scheme shown in fig. 3 of embodiment 3.

In the user heat exchange device 50 of the heat user 3 shown in the diagram b in fig. 4 of the present embodiment, the distribution water pump 5 is provided on the distribution water supply pipe 6 between the outlet of the confluence three-way flow rate adjusting valve 17 and the water side inlet end of the evaporator 10; however, in practical application, the distributing water pump 5 may be disposed on the distributing return pipe 7 between the water side outlet end of the evaporator 10 and the inlet end of the bypass pipe 23, and the suction end of the distributing water pump 5 is connected to the water side outlet end of the evaporator 10.

The connection mode of the converging three-way flow regulating valve 17 in the system is applicable to all the user heat exchange devices 50 which simultaneously use the water source heat pump 9 and the distribution water pump 5.

Example 5

As shown in fig. 5, the present embodiment is also a large temperature difference heating system using the present utility model, which is used in the occasion where there is a winter heating and a summer cooling demand. The heat source station 1 in this embodiment is a heat exchange station of an urban heat supply network; in the working process in winter, the thermal power plant is used as a heat source of the urban heat supply network, and the urban heat supply network water supply pipe 101 and the urban heat supply network water return pipe 100 are used for transmitting and distributing heat to the heat source station 1, and the urban heat supply network water supply pipe 101 and the urban heat supply network water return pipe 100 from the thermal power plant to the heat source station 1 are primary networks; the large temperature difference heating system using the present utility model shown in fig. 5 is a secondary network.

When the electric control valve 32 on the primary network side works in winter, the hot water flow of the primary network entering the plate heat exchanger 55 is regulated and controlled according to the outdoor air temperature by utilizing a climate compensation curve set in the controller of the heat source station 1, and the hot water temperature of the low-temperature side outlet of the plate heat exchanger 55 is regulated and controlled, namely: hot water outlet temperature at outlet end a of heat source station 1.

The system shown in fig. 5 has two heat users 3 in common, namely: the hot user 3 shown in figures a, b of figure 5; the user inlets of both heat users 3 use the user heat exchange device 50 according to the utility model.

The hot user 3 shown in fig. 5 a is only used for heating the user in winter; whereas the heat consumer 3 shown in fig. 5 b is not only used for winter consumer heating, but also for summer cooling of the heat consumer 3; different types of water source heat pumps 9 are used in the user heat exchange means 50 of the two heat users 3, respectively;

For the heat consumer 3 shown in fig. 5 b, the water source heat pump 9 in the consumer heat exchange device 50 is a dual-purpose water source heat pump for cooling and heating, while for the heat consumer 3 shown in fig. 5 a, the water source heat pump 9 in the consumer heat exchange device 50 is a single-heat water source heat pump; compared with a single-heat type water source heat pump, the cold-hot dual-purpose water source heat pump is added with a four-way valve 45 in a refrigerant system; in addition, in order to discharge the cooling condensation heat generated by the cooling of the water source heat pump 9 in summer into the atmosphere; the closed cooling tower 44, the first ball valve 42 and the second ball valve 43 are also added to the user heat exchange device 50 of the heat user 3 shown in the diagram b in fig. 5.

The user heat exchange device 50 of the heat user 3 shown in fig. 5 a consists of the following parts: a water supply pipe 4, a distribution water supply pipe 6, a distribution water return pipe 7, a distribution water pump 5, a water source heat pump 9, an indoor water pump 21 and a converging three-way flow regulating valve 17; the water source heat pump 9 comprises four parts, namely an evaporator 10, a condenser 11, a compressor 12 and a throttle valve 13.

The user heat exchange device 50 of the heat user 3 shown in fig. 5 b consists of the following parts: a water supply pipe 4, a distribution water supply pipe 6, a distribution water return pipe 7, a distribution water pump 5, a water source heat pump 9, an indoor water pump 21, a split-flow three-way flow regulating valve 18, a closed cooling tower 44, a first ball valve 42 and a second ball valve 43; the water source heat pump 9 comprises five parts, namely an evaporator 10, a condenser 11, a compressor 12, a throttle valve 13 and a four-way valve 45.

The following is the working process of the large temperature difference heating system of FIG. 5 in winter and summer; the working process of the user heat exchange device 50 according to the utility model can also be seen from the working process of the heat user 3 shown in figures a, b.

(1) FIG. 5 shows a winter operation using the large temperature difference heating system of the present utility model

The circulating pump 2 is a variable frequency pump and works normally in winter. In operation, the actual hot water temperature at the outlet end of the water supply pipe 4 detected by the backwater temperature sensor 22 is transmitted to the controller of the heat source station 1 and is compared with the hot water temperature expected value at the outlet end of the water supply pipe 4 set by the controller; according to the comparison result, the flow rate of the hot water in the water supply pipe 4 is regulated by changing the operation frequency of the circulation pump 2, so that the actual hot water temperature at the outlet end of the water supply pipe 4 is within a desired range.

During winter operation, the closed cooling tower 44 is not in operation; the two first ball valves 42 are closed and the second ball valve 43 is fully opened; for the user heat exchange device 50 of the heat user 3 shown in the diagram b in fig. 5, the refrigerant system connection relationship of the water source heat pump 9 is: the outlet end of the compressor 12 is connected with the suction end of the compressor 12 through a high-pressure node of the four-way valve 45, a reversing node of the four-way valve 45, the condenser 11, the throttle valve 13, the evaporator 10, a reversing node of the four-way valve 45 and a low-pressure node of the four-way valve 45 in sequence.

During winter operation, the working process of the large temperature difference heating system using the utility model shown in fig. 5 is as follows, and the working process of the heat user 3 shown in fig. a and b can be seen from the working process of the user heat exchanging device 50 of the utility model:

In operation, hot water heated by the heat source station 1 sequentially enters the water supply pipe 4 through the outlet end A of the heat source station 1 and the inlet end of the water supply pipe 4, flows into the user heat exchange device 50 of the heat user 3 shown in the diagram a in fig. 5 through the water supply pipe 4, and is divided into two paths; the first hot water does not enter the evaporator 10 of the user heat exchange device 50 for heat dissipation, but sequentially passes through the connection point of the inlet end of the distribution water supply pipe 6 and the water supply pipe 4, the connection point of the outlet end of the distribution water return pipe 7 and the water supply pipe 4, and enters the water supply pipe 4 at the downstream of the user heat exchange device 50;

The second hot water sequentially passes through the inlet end of the distribution water supply pipe 6 and the side inflow port of the converging three-way flow regulating valve 17 and enters the converging three-way flow regulating valve 17; the mixed water is mixed with part of low-temperature hot water from the distribution return pipe 7 and sequentially passes through the bypass pipe 23 and the direct-current inlet of the converging three-way flow regulating valve 17, and returns to the converging three-way flow regulating valve 17, so that the regulation and control of the temperature of the hot water at the water side inlet end of the evaporator 10 are realized; the mixed hot water sequentially passes through the outlet of the converging three-way flow regulating valve 17, the suction end of the distribution water pump 5, the extrusion end of the distribution water pump 5, the outlet end of the distribution water supply pipe 6 and the water side inlet end of the evaporator 10, and enters the evaporator 10 to perform indirect heat exchange with the refrigerant; after the heat quantity of the hot water is released and the water temperature is reduced, the low-temperature hot water sequentially passes through the water side outlet end of the evaporator 10 and the inlet end of the distribution return pipe 7; enters a distribution return pipe 7 and is divided into two parts of low-temperature hot water;

A part of low-temperature water sequentially passes through the inlet end of the bypass pipe 23, the outlet end of the bypass pipe 23 and the direct-current inlet of the converging three-way flow regulating valve 17 and returns to the converging three-way flow regulating valve 17; the other part of low-temperature water flows into the water supply pipe 4 at the downstream of the user heat exchange device 50 through the outlet end of the distribution return pipe 7; heat is dissipated from the evaporator 10 which does not enter the user heat exchange device 50, and flows into the first path of hot water downstream of the user heat exchange device 50 through the water supply pipe 4 between the inlet end of the distribution water supply pipe 6 and the outlet end of the distribution water return pipe 7 of the user heat exchange device 50; the hot water is mixed and flows out of the user heat exchange device 50 of the heat user 3 shown in the diagram a in fig. 5, and then flows into the user heat exchange device 50 of the heat user 3 shown in the diagram b in fig. 5 along the water supply pipe 4, and is divided into two paths;

The first hot water does not enter the evaporator 10 of the user heat exchange device 50 for heat dissipation, but sequentially passes through the connection point of the inlet end of the distribution water supply pipe 6 and the water supply pipe 4, the connection point of the outlet end of the distribution water return pipe 7 and the water supply pipe 4, and enters the water supply pipe 4 at the downstream of the user heat exchange device 50; the second path of hot water enters the distribution water supply pipe 6 through the inlet end of the distribution water supply pipe 6, directly flows out of the straight flow outlet of the diversion three-way flow regulating valve 18, sequentially passes through the inlet end of the bypass pipe 23 and the outlet end of the bypass pipe 23, and returns to the distribution water supply pipe 6 for mixing, so that the regulation and control of the hot water temperature at the water side inlet end of the evaporator 10 of the user heat exchange device 50 are realized; the mixed hot water sequentially passes through a second ball valve 43, a suction end of a distribution water pump 5, an extrusion end of the distribution water pump 5, an outlet end of a distribution water supply pipe 6 and a water side inlet end of an evaporator 10, and enters the evaporator 10 to perform indirect heat exchange with the refrigerant; after the heat quantity of the hot water is released and the water temperature is reduced, the low-temperature hot water sequentially passes through the water side outlet end of the evaporator 10, the inlet end of the distribution return pipe 7 and the inlet of the distribution three-way flow regulating valve 18; the hot water enters a split-flow three-way flow regulating valve 18 and is divided into two parts of low-temperature hot water;

A part of low-temperature water sequentially passes through a straight outflow port of the diversion three-way flow regulating valve 18, an inlet end of the bypass pipe 23 and an outlet end of the bypass pipe 23 and returns to the distribution water supply pipe 6; the other part of low-temperature water sequentially passes through the side flow outlet of the diversion three-way flow regulating valve 18 and the outlet end of the distribution return pipe 7 and also flows into the water supply pipe 4 at the downstream of the user heat exchange device 50; heat is dissipated from the evaporator 10 which does not enter the user heat exchange device 50, and flows into the first path of hot water downstream of the user heat exchange device 50 through the water supply pipe 4 between the inlet end of the distribution water supply pipe 6 and the outlet end of the distribution water return pipe 7 of the user heat exchange device 50; the two paths of hot water are mixed in the water supply pipe 4, come out of the user heat exchange device 50 of the heat user 3 shown in the diagram B in fig. 5, sequentially pass through the suction end of the circulating pump 2, the extrusion end of the circulating pump 2, the outlet end of the water supply pipe 4 and the inlet end B of the heat source station 1, return to the heat source station 1 to be heated again, and sequentially enter the water supply pipe 4 through the outlet end A of the heat source station 1 and the inlet end of the water supply pipe 4; the winter working cycle of the large-temperature-difference heating system using the utility model shown in fig. 5 is completed once.

In winter operation, the indoor system workflow of the heat consumer 3 shown in fig. 5 a, and the refrigerant workflow of the water source heat pump 9 are the same as the heat consumer 3 shown in fig. 3 b. The indoor system workflow of the heat user 3 shown in fig. 5, b, is also the same as the heat user 3 shown in fig. 3, b.

When the large-temperature-difference heating system shown in fig. 5 is used for realizing large-temperature-difference operation in the working process in winter, the temperature of hot water at the outlet end of the water supply pipe 4 is lower; therefore, through the heat exchange of the plate heat exchanger 55, the temperature of the hot water in the urban heat supply network water return pipe 100 can be reduced, so that the hot water temperature difference between the urban heat supply network water supply pipe 101 and the urban heat supply network water return pipe 100 is increased, and the primary network also realizes large temperature difference heat supply.

(2) FIG. 5 shows a summer operation of a large temperature difference heating system employing the present utility model

The circulating pump 2 does not work in summer; however, the secondary network constant-pressure water supplementing system in the heat source station 1 works normally, and the pressure of the constant-pressure point is maintained to be a preset expected value, namely: the pressure in the water supply pipe 4 is maintained.

In summer operation, the hot user 3 shown in figure 5 a is not working; the hot user 3 shown in fig. 5 b works normally and supplies cold to the user. The closed cooling tower 44 operates normally; the two first ball valves 42 are fully open and the second ball valve 43 is closed.

For the user heat exchange device 50 of the heat user 3 shown in the diagram b in fig. 5, the bypass outlet of the split three-way flow regulating valve 18 is closed, and the direct outlet of the split three-way flow regulating valve 18 is fully opened; the connection relation of the refrigerant system of the water source heat pump 9 is as follows: the outlet end of the compressor 12 is connected with the suction end of the compressor 12 through a high-pressure node of the four-way valve 45, a reversing node of the four-way valve 45, the evaporator 10, the throttle valve 13, the condenser 11, a reversing node of the four-way valve 45 and a low-pressure node of the four-way valve 45 in sequence.

In operation, the evaporator 10 becomes a condenser for cooling the high temperature, high pressure refrigerant gas discharged from the compressor into a refrigerant liquid; and the condenser 11 becomes an evaporator for producing chilled water for cooling the user.

In operation, in order to maintain the water pressure of the indoor system of the heat consumer 3 shown in the diagram b in fig. 5, a water make-up pump is provided in the consumer heat exchange device 50 of the heat consumer 3 shown in the diagram b in fig. 5 to make up water and fix the pressure for the indoor system of the heat consumer 3. The suction end of the water supplementing pump is connected with the water supply pipe 4, and the pressing end of the water supplementing pump is connected with the suction end of the indoor water pump 21.

When working in summer, the refrigerating work flow of the heat user 3 in summer shown in the graph b in fig. 5 is divided into three parts, which are respectively as follows; the operation of the user heat exchange device 50 is also known from this:

(1) The working flow of the cooling water is as follows: during operation, cooling water from the outlet end of the closed cooling tower 44 sequentially passes through the first ball valve 42, the suction end of the distribution water pump 5, the extrusion end of the distribution water pump 5, the outlet end of the distribution water supply pipe 6 and the water side inlet end of the evaporator 10, and enters the evaporator 10 to perform indirect heat exchange with the refrigerant; after the water temperature rises, the cooling water sequentially passes through the water side outlet end of the evaporator 10, the inlet end of the distribution return pipe 7, the inlet of the distribution three-way flow regulating valve 18, the straight outflow end of the distribution three-way flow regulating valve 18, the inlet end of the bypass pipe 23, the outlet end of the bypass pipe 23, the first ball valve 42 and the inlet end of the closed cooling tower 44, enters the closed cooling tower 44, indirectly exchanges heat with circulating spray water and air, emits heat to be cooled, and then enters the outlet end of the closed cooling tower 44, so that one cooling water cycle is completed.

(2) The water source heat pump 9 refrigerant system duty cycle is as follows: during operation, the high-temperature high-pressure refrigerant superheated gas discharged from the outlet end of the compressor 12 sequentially passes through the high-pressure node of the four-way valve 45 and the reversing node of the four-way valve 45, and enters the evaporator 10 to perform indirect heat exchange with cooling water; the refrigerant gives off heat and is cooled to liquid; after the refrigerant liquid comes out of the evaporator 10, the refrigerant liquid enters the throttle valve 13 and is throttled into a low-temperature low-pressure refrigerant gas-liquid two-phase mixture; then enters a condenser 11 to perform indirect heat exchange with indoor system backwater, and the refrigerant gas-liquid two-phase mixture is gasified into low-temperature low-pressure refrigerant gas after absorbing heat of the indoor system backwater; then sequentially passes through a reversing node of the four-way valve 45, a low-pressure node of the four-way valve 45 and the suction end of the compressor 12, enters the compressor 12 and is compressed again, and thus the working cycle of the refrigerant system of the primary water source heat pump 9 is completed.

(3) The summer duty cycle of the indoor system is as follows: the indoor system backwater from the outlet end of the indoor heat dissipation end 20 sequentially passes through the indoor backwater pipe 25, the suction end of the indoor water pump 21, the extrusion end of the indoor water pump 21 and the water side inlet end of the condenser 11, enters the condenser 11, and is subjected to indirect heat exchange with the low-temperature low-pressure refrigerant gas-liquid two-phase mixture from the throttle valve 13, and after the temperature reaches the requirement of the indoor system water supply temperature, the backwater sequentially passes through the water side outlet end of the condenser 11, the indoor water supply pipe 24 and the indoor heat dissipation end 20 inlet end and enters the indoor heat dissipation end 20 to cool a user; after the indoor heat is absorbed and the temperature is increased, the indoor heat is returned to the indoor water return pipe 25 through the outlet end of the indoor heat dissipation tail end 20, so that the summer working cycle of the indoor system is completed.

As can be seen from the above description of the present embodiment: in the summer cooling work process of the large-temperature difference heating system shown in fig. 5, only the constant-pressure water supplementing system in the heat source station 1 and the heat user 3 shown in the diagram b in fig. 5 needing cooling work normally; other heat users 3 and other devices of the secondary network in fig. 5 and the primary network stop working, so the summer cooling working process of the large-temperature difference heating system using the utility model shown in fig. 5 is the scattered cooling by taking each heat user 3 as a unit, and the winter heating is the central heating of the city; therefore, the large temperature difference heating system shown in fig. 5 is realized by 'centralized heating in winter and decentralized cooling in summer'; therefore, compared with the conventional urban concentrated cooling and heating system, the system has higher cooling performance in summer and better economic benefit; the heat of central heating in cities is excellent in winter; when the urban central heating system using the thermal power plant and the like as heat sources in winter is used, the large temperature difference operation of the primary and secondary networks can be realized simultaneously.

In the user heat exchange device 50 of the heat user 3 shown in fig. a of fig. 5 of the present embodiment, the distribution water pump 5 is provided on the distribution water supply pipe 6 between the outlet of the confluent three-way flow regulating valve 17 and the water side inlet end of the evaporator 10; however, in practical application, the distributing water pump 5 may be disposed on the distributing return pipe 7 between the water side outlet end of the evaporator 10 and the inlet end of the bypass pipe 23, and the suction end of the distributing water pump 5 is connected to the water side outlet end of the evaporator 10.

In the user heat exchange device 50 of the heat user 3 shown in the diagram b of fig. 5 of the present embodiment, the distribution water pump 5 is provided on the distribution water supply pipe 6 between the water side inlet end of the evaporator 10 and the second ball valve 43. However, in practical application, the following two setting modes are provided: 1) The distribution water pump 5 is arranged on the distribution water supply pipe 6 between the second ball valve 43 and the outlet end of the bypass pipe 23, and the suction end of the distribution water pump 5 is connected with the outlet end of the bypass pipe 23; 2) The distribution water pump 5 is arranged on the distribution water return pipe 7 between the water side outlet end of the evaporator 10 and the inlet of the diversion three-way flow regulating valve 18, and the suction end of the distribution water pump 5 is connected with the water side outlet end of the evaporator 10.

Example 6

As shown in fig. 6, this embodiment is also a large temperature difference heating system using the present utility model, which is used in the occasions where there is a heating demand. The heat source station 1 in this embodiment is a geothermal well heat exchange station; the connection mode of the heat source station 1 is as follows: the high-temperature side inlet end of the underground water heat exchanger 34 is connected with a submerged pump 35 in the pumping well 31, and the high-temperature side outlet end of the underground water heat exchanger 34 is connected with the recharging well 33; the low-temperature side inlet end of the groundwater heat exchanger 34 is connected with the inlet end B of the heat source station 1, and the low-temperature side outlet end of the groundwater heat exchanger 34 is connected with the outlet end A of the heat source station 1. The circulation pump 2 is a variable frequency pump.

As shown in fig. 6, the system has two heat users 3 in common, namely: the hot user 3 shown in figures a, b of figure 6; the user inlet of the heat consumer 3 shown in figure b uses the consumer heat exchange device 50 according to the utility model.

As shown in fig. 6, the user heat exchange device 50 of the heat user 3 shown in fig. 6 b differs from the user heat exchange device 50 of the heat user 3 shown in fig. 3 b in that: a preheater 19 is added to the consumer heat exchange device 50.

The preheater 19 functions in operation: the hot water in the upstream water supply pipe 4 is utilized to preheat the indoor system backwater of the heat user 3, so as to reduce the operation energy consumption of the water source heat pump 9 in the user heat exchange device 50.

The connection mode of the preheater 19 in the user heat exchange device 50 is as follows: the inlet end of the high temperature side of the preheater 19 is connected with the water supply pipe 4 through the inlet end of the distribution water supply pipe 6, and the outlet end of the high temperature side of the preheater 19 is connected with the outlet end of the bypass pipe 23; the inlet end of the low-temperature side of the preheater 19 is connected with the indoor water return pipe 25 of the heat user 3, and the outlet end of the low-temperature side of the preheater 19 is sequentially connected with the inlet end of the water side of the condenser 11 of the user heat exchange device 50 through the suction end of the indoor water pump 21 and the extrusion end of the indoor water pump 21.

In practical applications, when the indoor water pump 21 is disposed at the water side outlet of the condenser 11 of the user heat exchange device 50, the low temperature side outlet of the preheater 19 is connected to the water side inlet of the condenser 11, and other connection relationships of the preheater 19 are unchanged.

In the working process, the working flow of the large-temperature difference heating system using the utility model shown in fig. 6 is as follows; the working process of the user heat exchange device 50 according to the utility model can also be seen from the working process of the heat user 3 shown in the diagram b:

In operation, hot water from the heat source station 1 sequentially enters the water supply pipe 4 through the outlet end A of the heat source station 1 and the inlet end of the water supply pipe 4, flows to the heat user 3 shown in the diagram a in fig. 6 through the water supply pipe 4, and is divided into two paths; the first hot water sequentially passes through the connection point of the inlet end of the distribution water supply pipe 6 and the water supply pipe 4, the connection point of the outlet end of the distribution water return pipe 7 and the water supply pipe 4, and enters the water supply pipe 4 at the downstream of the connection point of the outlet end of the distribution water return pipe 7 and the water supply pipe 4; the second hot water sequentially passes through the inlet end of the distribution water supply pipe 6 and the direct-current inlet of the converging three-way flow regulating valve 17, enters the converging three-way flow regulating valve 17, and is mixed with hot water from the distribution water return pipe 7 and also enters part of the converging three-way flow regulating valve 17 through the bypass pipe 23 and the side inflow port of the converging three-way flow regulating valve 17, so that the regulation and control of the temperature of the hot water at the inlet end of the indoor heat dissipation tail end 20 of the heat user 3 (namely, the regulation and control of the indoor system water supply temperature of the heat user 3) are realized; the mixed hot water sequentially passes through the outlet of the converging three-way flow regulating valve 17, the outlet end of the distribution water supply pipe 6 and the inlet end of the indoor heat dissipation tail end 20, and enters the indoor heat dissipation tail end 20 to heat a user; after the heat released by the hot water and the water temperature are reduced, the low-temperature hot water is divided into two parts of low-temperature hot water through an outlet end of an indoor heat dissipation tail end 20, an inlet end of a distribution return pipe 7, an intake end of a distribution water pump 5 and an extrusion end of the distribution water pump 5 in sequence; a part of low-temperature water sequentially passes through the inlet end of the bypass pipe 23 and the outlet end of the bypass pipe 23 and returns to the side inflow port of the converging three-way flow regulating valve 17; the other part of low-temperature water flows into the water supply pipe 4 at the downstream of the heat user 3 through the outlet end of the distribution return pipe 7; heat is dissipated from the indoor heat dissipation end 20 which does not enter the heat consumer 3, and the first path of hot water which flows into the downstream through the water supply pipe 4 between the inlet end of the distribution water supply pipe 6 and the outlet end of the distribution water return pipe 7 is mixed; after mixing, the hot water continues to flow downstream along the water supply pipe 4, flows into the user heat exchange device 50 of the heat user 3 shown in the diagram b in fig. 6, and is divided into two paths;

The first hot water does not enter the evaporator 10 of the user heat exchange device 50 for heat dissipation, but sequentially passes through the connection point of the inlet end of the distribution water supply pipe 6 and the water supply pipe 4, the connection point of the outlet end of the distribution water return pipe 7 and the water supply pipe 4, and enters the water supply pipe 4 at the downstream of the user heat exchange device 50;

The second hot water sequentially passes through the inlet end of the distribution water supply pipe 6 and the high-temperature side inlet end of the preheater 19, and enters the preheater 19 to preheat indoor system backwater; the hot water emits heat, after the water temperature is reduced, the hot water flows out of the preheater 19 through the outlet end at the high temperature side of the preheater 19, then flows out of the bypass outlet of the split three-way flow regulating valve 18, and sequentially flows through the inlet end of the bypass pipe 23 and the outlet end of the bypass pipe 23, and returns to a part of the low-temperature hot water of the distribution water supply pipe 6 to be mixed, so that the regulation and control of the temperature of the hot water at the water side inlet end of the evaporator 10 of the user heat exchange device 50 are realized;

The mixed hot water sequentially passes through the outlet end of the distribution water supply pipe 6 and the water side inlet end of the evaporator 10, and enters the evaporator 10 to perform indirect heat exchange with the refrigerant; the hot water emits heat again, the water temperature is reduced again, and then the hot water sequentially passes through the outlet end of the water side of the evaporator 10, the inlet end of the distribution return pipe 7, the suction end of the distribution water pump 5, the extrusion end of the distribution water pump 5 and the inlet of the distribution three-way flow regulating valve 18, and enters the distribution three-way flow regulating valve 18 to be divided into two parts of low-temperature hot water;

A part of low-temperature water sequentially passes through a bypass outlet of the diversion three-way flow regulating valve 18, an inlet end of the bypass pipe 23 and an outlet end of the bypass pipe 23 and returns to the distribution water supply pipe 6; the other part of low-temperature water sequentially passes through the straight outflow port of the diversion three-way flow regulating valve 18 and the outlet end of the distribution return pipe 7 and also flows into the water supply pipe 4 at the downstream of the user heat exchange device 50;

Heat is dissipated from the evaporator 10 which does not enter the user heat exchange device 50, and flows into the first path of hot water downstream of the user heat exchange device 50 through the water supply pipe 4 between the inlet end of the distribution water supply pipe 6 and the outlet end of the distribution water return pipe 7 of the user heat exchange device 50; the hot water is mixed and after exiting the user heat exchange device 50 of the heat user 3 shown in the diagram b in fig. 6, the hot water continues to flow to the circulating pump 2 along the water supply pipe 4; after being pressurized by the circulating pump 2, the hot water sequentially passes through the outlet end of the water supply pipe 4 and the inlet end B of the heat source station 1, and returns to the heat source station 1 to be heated again, so that the working cycle of the large-temperature-difference heat supply system using the utility model shown in fig. 6 is completed.

In the above-described working cycle of the large temperature difference heating system using the present utility model, the indoor system work flow of the heat user 3 shown in the graph b of fig. 6 is as follows: indoor system backwater from the outlet end of the indoor heat dissipation tail end 20 sequentially passes through the indoor backwater pipe 25 and the low-temperature side inlet end of the preheater 19, and enters the preheater 19 to indirectly exchange heat with hot water with higher temperature from the water supply pipe 4 at the upstream of the heat user 3; after the absorbed heat is preheated, the preheated heat sequentially passes through a low-temperature side outlet end of the preheater 19, an intake end of the indoor water pump 21, an extrusion end of the indoor water pump 21 and a water side inlet end of the condenser 11, enters the condenser 11, and is subjected to indirect heat exchange with the refrigerant superheated gas from the compressor 12, the preheated indoor system backwater is heated again, and after the temperature reaches the indoor system water supply requirement, the preheated heat sequentially passes through the water side outlet end of the condenser 11, the indoor water supply pipe 24 and the indoor heat dissipation end 20 inlet end, and enters the indoor heat dissipation end 20 to supply heat for a user; after the temperature is reduced, the water returns to the indoor water return pipe 25 through the outlet end of the indoor heat dissipation end 20, so that one indoor system hot water circulation is completed.

In the user heat exchange device 50 of the heat user 3 shown in the diagram b in fig. 6 of the present embodiment, the distribution water pump 5 is provided on the distribution return pipe 7 between the inlet of the split three-way flow regulating valve 18 and the water side outlet end of the evaporator 10; however, in practice, the distribution water pump 5 may be disposed on the distribution water supply pipe 6 between the water side inlet end of the evaporator 10 and the outlet end of the bypass pipe 23, and the extrusion end of the distribution water pump 5 is connected to the water side inlet end of the evaporator 10.

Similarly, the user heat exchange device 50 of the heat user 3 shown in the graph b in fig. 4 can be further improved by adding a preheater 19 to the system. At this time, the connection mode of the preheater 19 of the user heat exchange device 50 in the system is: the inlet end of the high-temperature side of the preheater 19 is connected with the water supply pipe 4 through the inlet end of the distribution water supply pipe 6, and the outlet end of the high-temperature side of the preheater 19 is connected with the direct-current inlet of the converging three-way flow regulating valve 17; the inlet end of the low-temperature side of the preheater 19 is connected with the outlet end of the indoor heat dissipation end 20 of the heat user 3 through an indoor water return pipe 25, and the outlet end of the low-temperature side of the preheater 19 is connected with the inlet end of the water side of the condenser 11. The indoor water pump 21 of the user heat exchange device 50 may be provided at the water side inlet end of the condenser 11 or at the water side outlet end of the condenser 11. At this time, the method of setting the distribution water pump 5 in the user heat exchange device 50 has two methods: 1) The distribution water pump 5 is arranged on the distribution water supply pipe 6 between the outlet of the converging three-way flow regulating valve 17 and the water side inlet end of the evaporator 10, and the extrusion end of the distribution water pump 5 is connected with the water side inlet end of the evaporator 10; 2) The distributing water pump 5 can also be arranged on the distributing return pipe 7 between the water side outlet end of the evaporator 10 and the inlet end of the bypass pipe 23, and the suction end of the distributing water pump 5 is connected with the water side outlet end of the evaporator 10.

Similarly, for the user heat exchange device 50 of the heat user 3 shown in fig. a of embodiment 5, a preheater 19 may be added to the system, and the user heat exchange device 50 may be further improved. At this time, the connection manner of the preheater 19 in the user heat exchange device 50 is: the inlet end of the high-temperature side of the preheater 19 is connected with the water supply pipe 4 through the inlet end of the distribution water supply pipe 6, and the outlet end of the high-temperature side of the preheater 19 is connected with the side inflow port of the converging three-way flow regulating valve 17; the inlet end of the low-temperature side of the preheater 19 is connected with the outlet end of the indoor heat dissipation end 20 of the heat user 3 through an indoor water return pipe 25, and the outlet end of the low-temperature side of the preheater 19 is connected with the inlet end of the water side of the condenser 11. The indoor water pump 21 of the user heat exchange device 50 may be provided at the water side inlet end of the condenser 11 or at the water side outlet end of the condenser 11. At this time, the method of setting the distribution water pump 5 in the user heat exchange device 50 has two methods: 1) The distribution water pump 5 is arranged on the distribution water supply pipe 6 between the outlet of the converging three-way flow regulating valve 17 and the water side inlet end of the evaporator 10, and the extrusion end of the distribution water pump 5 is connected with the water side inlet end of the evaporator 10; 2) The distributing water pump 5 can also be arranged on the distributing return pipe 7 between the water side outlet end of the evaporator 10 and the inlet end of the bypass pipe 23, and the suction end of the distributing water pump 5 is connected with the water side outlet end of the evaporator 10.

Similarly, for the user heat exchange device 50 of the heat user 3 shown in the diagram b in the embodiment 5, a preheater 19 may be added to the system, and the user heat exchange device 50 may be further improved. At this time, the connection manner of the preheater 19 in the user heat exchange device 50 is: the inlet end of the high temperature side of the preheater 19 is connected with the water supply pipe 4 through the inlet end of the distribution water supply pipe 6, and the outlet end of the high temperature side of the preheater 19 is connected with the outlet end of the bypass pipe 23; the inlet end of the low-temperature side of the preheater 19 is connected with the outlet end of the indoor heat dissipation end 20 of the heat user 3 through an indoor water return pipe 25, and the outlet end of the low-temperature side of the preheater 19 is connected with the inlet end of the water side of the condenser 11. The indoor water pump 21 of the user heat exchange device 50 may be provided at the water side inlet end of the condenser 11 or at the water side outlet end of the condenser 11. At this time, the method of setting the distribution water pump 5 in the user heat exchange device 50 has three methods: 1) The distribution water pump 5 is arranged on the distribution water supply pipe 6 between the water side inlet end of the evaporator 10 and the second ball valve 43, and the extrusion end of the distribution water pump 5 is connected with the water side inlet end of the evaporator 10; 2) The distribution water pump 5 is arranged on the distribution water supply pipe 6 between the second ball valve 43 and the outlet end of the bypass pipe 23, and the suction end of the distribution water pump 5 is connected with the outlet end of the bypass pipe 23; 3) The distribution water pump 5 is arranged on the distribution water return pipe 7 between the water side outlet end of the evaporator 10 and the inlet of the diversion three-way flow regulating valve 18, and the suction end of the distribution water pump 5 is connected with the water side outlet end of the evaporator 10.

Example 7

As shown in fig. 7, this embodiment is also a large temperature difference heating system using the present utility model, which is used in the occasions where there is a heating demand. The heat source station 1 in this embodiment is a waste heat recovery device; the connection mode of the heat source station 1 is as follows: the high Wen Ceru port end of the waste heat recovery heat exchanger 36 is connected with the water intake pipe 37, and the high temperature side outlet end of the waste heat recovery heat exchanger 36 is connected with the water drain pipe 38; the low-temperature side inlet end of the waste heat recovery heat exchanger 36 is connected with the inlet end B of the heat source station 1, and the low-temperature side outlet end of the waste heat recovery heat exchanger 36 is connected with the outlet end A of the heat source station 1. The circulation pump 2 is a variable frequency pump.

As shown in fig. 7, the system has two heat users 3 in common, namely: the hot user 3 shown in figures a, b of figure 7; the user inlet of the heat consumer 3 shown in figure b uses the consumer heat exchange device 50 according to the utility model.

As shown in fig. 7, the user heat exchange device 50 of the heat user 3 shown in fig. 7 b is different from the user heat exchange device 50 of the heat user 3 shown in fig. 3 b in that: 1) The distributing water pump 5 of the user heat exchange device 50 is arranged on the distributing water supply pipe 6 between the water side inlet end of the evaporator 10 and the outlet end of the bypass pipe 23; 2) A buffer tank 41 is provided on the distribution return pipe 7 between the water side outlet end of the evaporator 10 of the consumer heat exchange device 50 and the inlet of the split three-way flow regulating valve 18.

In operation, the buffer tank 41 functions as: the split three-way flow regulating valve 18 can regulate and control the temperature of hot water at the water side inlet end of the evaporator 10 more stably. The buffer tank 41 may also be mounted on the bypass pipe 23.

The above-described method of setting the buffer tank 41 is still applicable when the distribution water pump 5 of the user heat exchange device 50 is provided on the distribution return pipe 7 between the water side outlet end of the evaporator 10 and the inlet of the split three-way flow regulating valve 18.

In operation, the working flow of the large temperature difference heating system using the utility model shown in fig. 7 is as follows, and the working flow of the user heat exchange device 50 of the utility model can be seen from the working flow of the heat user 3 shown in fig. b:

In operation, hot water from the heat source station 1 sequentially enters the water supply pipe 4 through the outlet end A of the heat source station 1 and the inlet end of the water supply pipe 4, flows to the heat user 3 shown in the figure a in figure 7 through the water supply pipe 4, and is divided into two paths; the first hot water sequentially passes through the connection point of the inlet end of the distribution water supply pipe 6 and the water supply pipe 4, the connection point of the outlet end of the distribution water return pipe 7 and the water supply pipe 4, and enters the water supply pipe 4 at the downstream of the connection point of the outlet end of the distribution water return pipe 7 and the water supply pipe 4; the second hot water enters the distribution water supply pipe 6 through the inlet end of the distribution water supply pipe 6, is mixed with a part of low-temperature hot water from the side stream outlet of the diversion three-way flow regulating valve 18 and also enters the distribution water supply pipe 6 through the bypass pipe 23, so that the regulation and control of the hot water temperature at the inlet end of the indoor heat dissipation tail end 20 of the heat user 3 (namely, the regulation and control of the indoor system water supply temperature of the heat user 3) are realized; the mixed hot water sequentially passes through the outlet end of the distribution water supply pipe 6 and the inlet end of the indoor heat dissipation tail end 20, and enters the indoor heat dissipation tail end 20 to heat a user; after the heat of the hot water is released and the water temperature is reduced, the low-temperature hot water sequentially passes through the outlet end of the indoor heat dissipation tail end 20, the inlet end of the distribution return pipe 7, the suction end of the distribution water pump 5, the extrusion end of the distribution water pump 5 and the inlet of the distribution three-way flow regulating valve 18, and enters the distribution three-way flow regulating valve 18 to be divided into two parts of low-temperature hot water;

A part of low-temperature water sequentially passes through a bypass outlet of the diversion three-way flow regulating valve 18, an inlet end of the bypass pipe 23 and an outlet end of the bypass pipe 23 and returns to the distribution water supply pipe 6; the other part of low-temperature water sequentially passes through a straight outflow port of the diversion three-way flow regulating valve 18 and an outlet end of the distribution return pipe 7 and also flows into the water supply pipe 4 at the downstream of the heat user 3; heat is dissipated from the indoor heat dissipation end 20 which does not enter the heat consumer 3, and the heat is mixed with the first path of hot water flowing into the downstream through the water supply pipe 4 between the inlet end of the distribution water supply pipe 6 and the outlet end of the distribution water return pipe 7 of the heat consumer 3;

After the two paths of hot water are mixed, the hot water continuously flows into the user heat exchange device 50 of the heat user 3 shown in the diagram b in fig. 7 along the water supply pipe 4 and is divided into two paths; the first hot water does not enter the evaporator 10 of the user heat exchange device 50 for heat dissipation, but sequentially passes through the connection point of the inlet end of the distribution water supply pipe 6 and the water supply pipe 4, the connection point of the outlet end of the distribution water return pipe 7 and the water supply pipe 4, and enters the water supply pipe 4 at the downstream of the user heat exchange device 50;

The second path of hot water enters the distribution water supply pipe 6 through the inlet end of the distribution water supply pipe 6, is mixed with a part of low-temperature hot water from the side outlet of the diversion three-way flow regulating valve 18 and also enters the distribution water supply pipe 6 through the bypass pipe 23, so that the regulation and control of the temperature of the hot water at the water side inlet end of the evaporator 10 of the user heat exchange device 50 are realized;

The mixed hot water sequentially passes through the suction end of the distribution water pump 5, the extrusion end of the distribution water pump 5, the outlet end of the distribution water supply pipe 6 and the water side inlet end of the evaporator 10, and enters the evaporator 10 to perform indirect heat exchange with the refrigerant; after the heat of the hot water is released and the water temperature is reduced, the low-temperature hot water sequentially passes through the water side outlet end of the evaporator 10, the inlet end of the distribution return pipe 7, the buffer water tank 41 and the inlet of the split-flow three-way flow regulating valve 18, and enters the split-flow three-way flow regulating valve 18 to be divided into two parts of low-temperature hot water;

a part of low-temperature hot water sequentially passes through a bypass outlet of the diversion three-way flow regulating valve 18, an inlet end of the bypass pipe 23 and an outlet end of the bypass pipe 23 and returns to the distribution water supply pipe 6 at the suction end of the distribution water pump 5; the other part of low-temperature water sequentially passes through the straight outflow port of the diversion three-way flow regulating valve 18 and the outlet end of the distribution return pipe 7 and also flows into the water supply pipe 4 at the downstream of the user heat exchange device 50; heat is dissipated from the evaporator 10 which does not enter the user heat exchange device 50, and flows into the first path of hot water downstream of the user heat exchange device 50 through the water supply pipe 4 between the inlet end of the distribution water supply pipe 6 and the outlet end of the distribution water return pipe 7 of the user heat exchange device 50;

The two paths of hot water are mixed and after exiting from the user heat exchange device 50 of the heat user 3 shown in the graph b in fig. 7, the mixture continues to flow to the circulating pump 2 along the water supply pipe 4; after being pressurized by the circulating pump 2, the hot water sequentially passes through the outlet end of the water supply pipe 4 and the inlet end B of the heat source station 1, and returns to the heat source station 1 to be heated again, so that the working cycle of the large-temperature-difference heat supply system using the utility model shown in figure 7 is completed.

In operation, the indoor system workflow of the heat consumer 3 shown in fig. 7 b, and the basic composition and refrigerant workflow of its water source heat pump 9 are the same as those of the heat consumer 3 shown in fig. 3 b of example 3.

The method for controlling the flow of hot water to the evaporator 10 of the user heat exchange device 50 of the heat user 3 shown in the graph b of fig. 7 is also the same as that of the heat user 3 shown in the graph b of the embodiment 3.

In practical use, the installation method of the buffer tank 41 in the present embodiment is also applicable to the user heat exchange device 50 of the heat user 3 shown in the diagram b in fig. 5, and the user heat exchange device 50 of the heat user 3 shown in the diagram b in fig. 6.

Similarly, for the user heat exchange device 50 of the heat user 3 shown in the diagram b in fig. 4 and the user heat exchange device 50 of the heat user 3 shown in the diagram a in fig. 5, a buffer water tank 41 can be added in the user heat exchange devices 50, so that the scheme of the user heat exchange device 50 is further improved; at this time, the buffer tank 41 is connected to the user heat exchanger 5 in two ways: 1) Is arranged on the bypass pipe 23; 2) And is arranged on the distribution return pipe 7 between the water side outlet end of the evaporator 10 and the inlet end of the bypass pipe 23.

For the user heat exchanger 50 of the heat consumer 3 shown in fig. b in fig. 4 and the user heat exchanger 50 of the heat consumer 3 shown in fig. a in fig. 5, the connection of the buffer water tank 41 in the user heat exchanger 50 is also applicable after adding a preheater 19 to the user heat exchanger 50.

Claims

1. The utility model provides a user heat transfer device, includes delivery pipe (4), distribution delivery pipe (6), distribution wet return (7), characterized by: the user heat exchange device also comprises a water source heat pump (9); the water source heat pump (9) comprises four parts, namely a compressor (12), an evaporator (10), a condenser (11) and a throttle valve (13); the outlet end of the compressor (12) is connected with the inlet end of the compressor (12) in sequence through the inlet end of the condenser (11) on the refrigerant side, the outlet end of the condenser (11) on the refrigerant side, the throttle valve (13), the inlet end of the evaporator (10) on the refrigerant side and the outlet end of the evaporator (10) on the refrigerant side, so as to form a water source heat pump (9) refrigerant circulation system;

The water side inlet end of the evaporator (10) is connected with the water supply pipe (4) through the outlet end of the distribution water supply pipe (6) and the inlet end of the distribution water supply pipe (6) in sequence; the water side outlet end of the evaporator (10) is connected with the water supply pipe (4) through the inlet end of the distribution return pipe (7) and the outlet end of the distribution return pipe (7) in sequence.

2. A user heat exchange device according to claim 1, characterized in that a preheater (19) is provided on the distribution water supply pipe (6) between the water side inlet end of the evaporator (10) and the inlet end of the distribution water supply pipe (6); the inlet end of the high-temperature side of the preheater (19) is connected with the water supply pipe (4) through the inlet end of the distribution water supply pipe (6), and the outlet end of the high-temperature side of the preheater (19) is connected with the inlet end of the water side of the evaporator (10); the low-temperature side outlet end of the preheater (19) is connected with the water side inlet end of the condenser (11).

3. The heat exchange device for users according to claim 1, wherein the bypass inlet of a converging three-way flow regulating valve (17) is connected with a distribution return pipe (7) between the water side outlet end of the evaporator (10) and the outlet end of the distribution return pipe (7) through the outlet end of a bypass pipe (23) and the inlet end of the bypass pipe (23) in sequence; the outlet of the converging three-way flow regulating valve (17) is connected with the water side inlet end of the evaporator (10) through the outlet end of the distribution water supply pipe (6); the direct-current inlet of the converging three-way flow regulating valve (17) is connected with the water supply pipe (4) through the inlet end of the distribution water supply pipe (6).

4. The user heat exchange device according to claim 1, characterized in that the direct current inlet of a converging three-way flow regulating valve (17) is connected with the distribution return pipe (7) between the water side outlet end of the evaporator (10) and the outlet end of the distribution return pipe (7) sequentially through the outlet end of a bypass pipe (23) and the inlet end of the bypass pipe (23); the outlet of the converging three-way flow regulating valve (17) is connected with the water side inlet end of the evaporator (10) through the outlet end of the distribution water supply pipe (6); the side inflow port of the converging three-way flow regulating valve (17) is connected with the water supply pipe (4) through the inlet end of the distribution water supply pipe (6).

5. A user heat exchange device according to claim 1, characterized in that the bypass outlet of a bypass three-way flow regulating valve (18) is connected to the distribution water supply pipe (6) between the water side inlet end of the evaporator (10) and the inlet end of the distribution water supply pipe (6) in sequence through the inlet end of a bypass pipe (23) and the outlet end of the bypass pipe (23); the inlet of the split three-way flow regulating valve (18) is connected with the water side outlet end of the evaporator (10) through the inlet end of the distribution return pipe (7); the straight outflow port of the split three-way flow regulating valve (18) is connected with the water supply pipe (4) through the outlet end of the distribution return pipe (7).

6. A user heat exchange device according to claim 1, characterized in that the straight outflow port of a split three-way flow regulating valve (18) is connected to the distribution water supply pipe (6) between the water side inlet port of the evaporator (10) and the inlet port of the distribution water supply pipe (6) sequentially through the inlet port of a bypass pipe (23) and the outlet port of the bypass pipe (23); the inlet of the split three-way flow regulating valve (18) is connected with the water side outlet end of the evaporator (10) through the inlet end of the distribution return pipe (7); the bypass outlet of the split three-way flow regulating valve (18) is connected with the water supply pipe (4) through the outlet end of the distribution return pipe (7).

7. A user heat exchange device according to claim 1, characterized in that a resistance valve (16) is arranged on the water supply pipe (4) between the inlet end of the distribution water supply pipe (6) and the outlet end of the distribution return pipe (7).

8. A user heat exchange device according to claim 2, characterized in that a resistance valve (16) is arranged on the water supply pipe (4) between the inlet end of the distribution water supply pipe (6) and the outlet end of the distribution return pipe (7).

9. A user heat exchange device according to claim 3, characterized in that a preheater (19) is arranged on the distribution water supply pipe (6) between the direct current inlet of the converging three-way flow regulating valve (17) and the inlet end of the distribution water supply pipe (6); the inlet end of the high-temperature side of the preheater (19) is connected with the water supply pipe (4) through the inlet end of the distribution water supply pipe (6), and the outlet end of the high-temperature side of the preheater (19) is connected with the direct-current inlet of the converging three-way flow regulating valve (17); the low-temperature side outlet end of the preheater (19) is connected with the water side inlet end of the condenser (11).

10. The user heat exchange device according to claim 4, characterized in that a preheater (19) is arranged on the distribution water supply pipe (6) between the side inflow port of the confluence three-way flow regulating valve (17) and the inlet end of the distribution water supply pipe (6); the inlet end of the high-temperature side of the preheater (19) is connected with the water supply pipe (4) through the inlet end of the distribution water supply pipe (6), and the outlet end of the high-temperature side of the preheater (19) is connected with the side inflow port of the converging three-way flow regulating valve (17); the low-temperature side outlet end of the preheater (19) is connected with the water side inlet end of the condenser (11).

11. A consumer heat exchange device according to claim 5 or 6, characterized in that a preheater (19) is provided on the distribution water supply pipe (6) between the outlet end of the bypass pipe (23) and the inlet end of the distribution water supply pipe (6); the inlet end of the high-temperature side of the preheater (19) is connected with the water supply pipe (4) through the inlet end of the distribution water supply pipe (6), and the outlet end of the high-temperature side of the preheater (19) is connected with the outlet end of the bypass pipe (23); the low-temperature side outlet end of the preheater (19) is connected with the water side inlet end of the condenser (11).