CN109708337B - Multistage series compression heat pump unit - Google Patents

Multistage series compression heat pump unit Download PDF

Info

Publication number
CN109708337B
CN109708337B CN201910159962.4A CN201910159962A CN109708337B CN 109708337 B CN109708337 B CN 109708337B CN 201910159962 A CN201910159962 A CN 201910159962A CN 109708337 B CN109708337 B CN 109708337B
Authority
CN
China
Prior art keywords
stage
evaporator
condenser
compressor
water
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Active
Application number
CN201910159962.4A
Other languages
Chinese (zh)
Other versions
CN109708337A (en
Inventor
张世钢
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Beijing Reke Energy Technology Research Co ltd
Original Assignee
Beijing Reke Energy Technology Research Co ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Beijing Reke Energy Technology Research Co ltd filed Critical Beijing Reke Energy Technology Research Co ltd
Priority to CN201910159962.4A priority Critical patent/CN109708337B/en
Publication of CN109708337A publication Critical patent/CN109708337A/en
Application granted granted Critical
Publication of CN109708337B publication Critical patent/CN109708337B/en
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Abstract

The invention discloses a multistage series compression heat pump unit, which comprises a first-stage condenser or a multistage condenser, a first-stage evaporator or a multistage evaporator, a refrigerant throttling device, a compressor and at least one-stage evaporator throttling device, wherein at least one stage of low-temperature low-pressure-ratio compressor or at least one stage of condenser throttling device and at least one stage of high-temperature low-pressure-ratio compressor are arranged. The multistage tandem compression heat pump unit disclosed by the invention has the advantages that hot water is subjected to tandem cascade heating in a multistage condenser, cold water is subjected to tandem cascade cooling in a multistage tandem evaporator, so that irreversible loss in the heat transfer process is greatly reduced, in addition, all unit units of the multistage heat pump unit are integrated, the performance difference among all unit units is reduced, the design and the use of the heat pump unit are more convenient and standard, the pressure ratio of each stage of compressor is reduced, the flow of the compressor is improved, and the application of a high-efficiency impeller compressor is facilitated.

Description

Multistage series compression heat pump unit
Technical Field
The invention relates to the field of heating and heat supply, in particular to a multistage series compression heat pump unit.
Background
With the wide application of heat pump devices in heating systems, refrigeration systems and hot water supply systems, heat pump devices such as water-water compression heat pumps, heat pump cold and hot water units, compression heat exchange units and the like have been developed unprecedentedly. In order to reduce the energy consumption for transportation, save water and reduce the initial investment of a transportation and distribution system, the heat pump devices generally adopt a heating/cooling mode with large temperature difference and small flow. However, when the temperature of the inlet water is constant, if a heating/cooling system with a large temperature difference and a small flow rate is realized, it is necessary to make the temperature of the hot water supply as high as possible and the temperature of the cold water outlet as low as possible. For the existing heat pump device, the heating/cooling mode with large temperature difference and small flow can cause the increase of condensing pressure and the reduction of evaporating pressure, which leads to the reduction of system performance coefficient and the reduction of energy utilization efficiency.
In order to solve the above problems, the chinese invention patent "a multistage series connection large temperature difference compression heat pump unit", the chinese invention patent "a large temperature rise compression heat pump unit" with the application number of CN200810104200.6, and the chinese utility model patent "a hot water heat pump unit with the application number of CN 200720149298.8" all provide a heat supply/cold supply mode of multistage heat pump series connection step temperature rise and step temperature drop, which improves the efficiency of large temperature difference and small flow heat pump unit to a certain extent, but in practical application, such heat pump unit still has the following problems:
(1) the heat pump units are combined into unit units by four parts, namely an evaporator, a condenser, a compressor and a throttling device (an expansion valve or a capillary tube and the like), and then the unit units form a whole machine.
(2) At present, the heat pump units applying the large temperature difference and small flow technology disperse the total capacity into a plurality of heat pumps for bearing, so that the flow of refrigerant conveyed by each compressor is too small, and the cooling and heating efficiency is low.
(3) Under the condition that a heat source or a cold source needs to provide large temperature difference and small flow on one side and small temperature difference and large flow on the other side, the existing heat pump units cannot be realized at present, or the cost is too high even if the existing heat pump units can be realized.
Disclosure of Invention
The invention aims to provide a multistage series compression heat pump unit, which is used for solving the problems of poor universality, low energy efficiency, high input cost and the like of the existing heat pump unit based on a large-temperature-difference small-flow technology.
The invention provides a multistage series compression heat pump unit, which comprises at least one stage of condenser, at least one stage of evaporator, a refrigerant throttling device, a compressor and at least one stage of evaporator throttling device, wherein the at least one stage of low-temperature low-pressure-ratio compressor or the at least one stage of condenser throttling device is at least one stage of high-temperature low-pressure-ratio compressor; if the condenser is a multi-stage condenser, a hot water inlet is formed in a water inlet of the first-stage condenser, the multi-stage condensers are sequentially connected in series from a hot water inflow end to a hot water outflow end, and a hot water outlet is formed in a water outlet of the last-stage condenser; if the evaporator is a primary evaporator, a water inlet of the primary evaporator is set as a cold water inlet, and a water outlet of the primary evaporator is set as a cold water outlet; if the evaporator is a multi-stage evaporator, a cold water inlet is formed in a water inlet of the first-stage evaporator, the multi-stage evaporators are sequentially connected in series from a cold water inflow end to a cold water outflow end, and a cold water outlet is formed in a water outlet of the last-stage evaporator; the gas refrigerant outlet of the first-stage evaporator is communicated with the air inlet of the compressor, the air outlet of the compressor is communicated with the gas refrigerant inlet of the first-stage condenser, and the liquid refrigerant outlet of the first-stage condenser is connected with the liquid refrigerant inlet of the first-stage evaporator through the refrigerant throttling device, so that a main circulation loop is formed; the multistage series compression heat pump unit also comprises at least one stage of evaporator auxiliary circulation branch or/and at least one stage of condenser auxiliary circulation branch which are communicated with the main circulation loop; and each stage of evaporator auxiliary circulation branch is provided with at least one low-temperature low-pressure ratio compressor and at least one evaporator throttling device, and the condenser auxiliary circulation branch is provided with at least one condenser throttling device and at least one high-temperature low-pressure ratio compressor.
Furthermore, the multistage series compression heat pump unit comprises a primary evaporator auxiliary circulation branch, a primary evaporator throttling device, a primary low-temperature low-pressure ratio compressor and a secondary evaporator are arranged on the primary evaporator auxiliary circulation branch, and a liquid refrigerant inlet of the secondary evaporator is communicated with a liquid refrigerant outlet of the primary evaporator or a liquid refrigerant outlet of the primary condenser through the primary evaporator throttling device; and the gaseous refrigerant outlet of the second-stage evaporator is communicated with the main circulation loop through the first-stage low-temperature low-pressure ratio compressor.
Furthermore, the multistage series compression heat pump unit also comprises a multistage evaporator auxiliary circulation branch, wherein the ith-stage evaporator auxiliary circulation branch is provided with an ith-stage evaporator throttling device, an ith-stage low-temperature low-pressure-ratio compressor and an (i + 1) -stage evaporator, and a liquid refrigerant inlet of the (i + 1) -stage evaporator is communicated with a liquid refrigerant outlet of the ith-stage evaporator or a liquid refrigerant outlet of the first-stage condenser through the ith-stage evaporator throttling device; and a gas refrigerant outlet of the (i + 1) th-stage evaporator is communicated with a gas inlet of the (i) th-stage low-temperature low-pressure-ratio compressor, and a gas outlet of the (i) th-stage low-temperature low-pressure-ratio compressor is communicated with a gas refrigerant inlet of the (i) th-stage evaporator or a gas refrigerant outlet of the (i) th-stage evaporator is communicated with a connecting pipe of the gas inlet of the (i-1) th-stage low-temperature low-pressure-ratio compressor.
In the claims, the symbol "i" in the multistage condenser (4-1, 4-2, …, 4-n), the multistage evaporator (3-1, 3-2, …, 3-m), the i-th stage evaporator/condenser, and the i + 1-th stage evaporator/condenser indicates an arabic number of 1, 2, 3 … …, 1 ≦ i ≦ min (m, n), where n and m are natural numbers greater than 1, and the symbol "3-i" indicates a natural number added by 1 to the number represented by "i" in the corresponding numerals of 3-1, 3-2, …, 3-n, and the symbol "3-i" indicates a natural number added by 1 to the number represented by "i".
Furthermore, the multistage series compression heat pump unit comprises a first-stage condenser auxiliary circulation branch, a first-stage condenser throttling device, a first-stage high-temperature low-pressure-ratio compressor and a second-stage condenser are arranged on the first-stage condenser auxiliary circulation branch, and a second-stage condenser gaseous refrigerant inlet is communicated with the first-stage condenser gaseous refrigerant inlet or the first-stage condenser gaseous refrigerant outlet through the first-stage high-temperature low-pressure-ratio compressor; and the liquid refrigerant outlet of the second-stage condenser is communicated with the main circulation loop through a first-stage condenser throttling device.
Furthermore, the multistage series compression heat pump unit also comprises a multistage condenser auxiliary circulation branch, wherein a j-th stage condenser throttling device, a j-th stage high-temperature low-pressure ratio compressor and a j + 1-th stage condenser are arranged on the j-th stage condenser auxiliary circulation branch, and a j + 1-th stage condenser gaseous refrigerant inlet is communicated with a j-th stage condenser gaseous refrigerant outlet through the j-th stage high-temperature low-pressure ratio compressor; and a liquid refrigerant outlet of the j +1 th-stage condenser is communicated with a liquid refrigerant inlet of the j-th-stage condenser through a j-th-stage condenser throttling device or a liquid refrigerant outlet of the j-th-stage condenser is communicated with a liquid refrigerant inlet connecting pipe of a throttling device of the j-1 th-stage condenser or a liquid refrigerant inlet of the first-stage condenser.
The symbol "j" is expressed by the same method as the symbol "i".
Furthermore, the multistage series compression heat pump unit also comprises a multistage evaporator auxiliary circulation branch, wherein a first-stage evaporator throttling device and a low-temperature low-pressure-ratio compressor are arranged on the first-stage evaporator auxiliary circulation branch, an evaporator throttling device and a low-temperature low-pressure-ratio compressor are arranged on each stage of evaporator auxiliary circulation branch of the multistage evaporator auxiliary circulation branch, and a second-stage evaporator liquid refrigerant inlet is communicated with a first-stage evaporator liquid refrigerant outlet or a first-stage condenser liquid refrigerant inlet through the first-stage evaporator throttling device; the gaseous refrigerant outlet of the second-stage evaporator is communicated with the main circulation loop through the low-temperature low-pressure-ratio compressor; the liquid refrigerant inlet of the ith-stage evaporator is communicated with the liquid refrigerant outlet of the (i-1) th-stage evaporator or the liquid refrigerant outlet of the first-stage condenser through the throttling device of the ith-stage evaporator; and a gaseous refrigerant outlet of the (i + 1) th-stage evaporator is communicated with a gaseous refrigerant inlet of the (i) th-stage evaporator through the (i) th-stage low-temperature low-pressure-ratio compressor or a gaseous refrigerant outlet of the (i) th-stage evaporator is communicated with a connecting pipe of an air inlet of the (i-1) th-stage low-temperature low-pressure-ratio compressor.
Further, the multistage series compression heat pump unit comprises a water-water heat exchanger, and the water-water heat exchanger is communicated with the first-stage evaporator and/or the first-stage condenser. For example, the primary water inlet/outlet and the secondary water inlet/outlet of the water-water heat exchanger are communicated with the primary evaporator and/or the primary condenser.
Furthermore, a primary water outlet of the water-water heat exchanger is communicated with a water inlet of the primary evaporator, a primary water inlet of the water-water heat exchanger is used as a primary water inlet of the whole unit, and a water outlet of the last-stage evaporator is used as a primary water outlet of the whole unit; the hot water side inlet of the first-stage condenser is connected with the secondary water side inlet of the water-water heat exchanger in parallel to serve as a secondary water inlet of the whole unit, and the hot water side outlet of the last-stage condenser is connected with the secondary water side outlet of the water-water heat exchanger in parallel to serve as a secondary water outlet of the whole unit.
Further, the compressor is a high pressure ratio compressor, which may be piston, rotary, scroll, screw, centrifugal, or axial, among others.
Further, the multistage low-temperature low-pressure-ratio compressor is coaxially arranged, and the outside of the multistage low-temperature low-pressure-ratio compressor shares the same shell to form an integrated compressor with a multistage compression function.
Further, the integrated compressor is an impeller compressor.
The invention has the beneficial effects that:
the multistage tandem compression heat pump unit disclosed by the invention has the advantages that hot water is subjected to tandem cascade heating in a multistage condenser, and cold water is subjected to tandem cascade cooling in a multistage tandem evaporator, so that irreversible loss in the heat transfer process is greatly reduced, and the performance of a heat pump is improved. In addition, all the unit units of the heat pump unit can be integrated, so that the performance difference among the unit units is reduced, the design and the use of the heat pump unit are more convenient and standard, the input cost can be reduced, and the universality of the existing heat pump unit applying the large-temperature-difference small-flow technology is obviously improved.
The impeller compressor represented by centrifugal and axial flow has the advantages of high efficiency, small volume, smooth operation and the like, and has the defects that the flow of the delivered gas cannot be too small and the pressure ratio cannot be too high. The invention reduces the pressure ratio of each stage of compressor, improves the flow rate of the compressor, greatly improves the overall performance of the heat pump unit and is beneficial to the application of the high-efficiency impeller compressor in the heat pump unit by arranging the multistage compressors to be compressed in series.
The invention can flexibly select the stage numbers of the condenser and the evaporator according to the flow of the cold and heat source and the inlet and outlet temperatures, can provide a heat supply/cold supply mode that one side of the heat source or the cold source needs to provide large temperature difference and small flow and the other side needs to provide small temperature difference and large flow, and reduces the cost of the heat source or the cold source of the heat pump set for asymmetric application of large temperature difference and small flow.
Drawings
Fig. 1 is a schematic structural diagram of a two-stage evaporation tandem compression heat pump unit provided in embodiment 1 of the present invention;
fig. 2 is a schematic structural diagram of a three-stage evaporation tandem compression heat pump unit provided in embodiment 2 of the present invention;
fig. 3 is a schematic structural diagram of a three-stage evaporation series compression heat exchanger unit with a water-water heat exchanger according to embodiment 3 of the present invention.
Fig. 4 is a schematic structural diagram of a two-stage condensation tandem compression heat pump unit provided in embodiment 4 of the present invention;
FIG. 5 is a schematic structural diagram of a three-stage condensation tandem compression heat pump unit according to embodiment 5 of the present invention;
fig. 6 is a schematic structural diagram of a three-stage evaporation three-stage condensation tandem compression heat pump unit provided in embodiment 6 of the present invention.
Detailed Description
The following examples are intended to illustrate the invention, but are not intended to limit the scope of the invention.
Example 1: two-stage evaporation series compression heat pump unit
Embodiment 1 provides a two-stage evaporation tandem compression heat pump unit, as shown in fig. 1, the heat pump unit includes a first-stage evaporator 3-1, a second-stage evaporator 3-2, a first-stage condenser 4-1, a compressor 1, a first low-temperature low-pressure-ratio compressor 2-1, a refrigerant throttling device 5, and a first-stage evaporator throttling device 7-1.
Supply of cold and hot water
a. Cold water supply interface: the primary evaporator 3-1 is connected with the secondary evaporator 3-2 in series, specifically, a cold water inlet is communicated with a water inlet of the primary evaporator 3-1 or a water inlet of the primary evaporator 3-1 is used as a cold water inlet of the whole unit, a water outlet of the secondary evaporator 3-2 is used as a cold water outlet of the whole unit, the cold water outlet is a cold water outlet of the whole unit, and a water outlet of the primary evaporator 3-1 is connected with a water inlet of the secondary evaporator 3-2 in series through a pipeline.
b. A hot water supply interface: the hot water inlet and the hot water outlet are respectively and directly communicated with the water inlet and the water outlet of the primary condenser 4-1 or the water inlet and the water outlet of the primary condenser 4-1 are used as the hot water inlet and the hot water outlet of the whole unit.
c. Cold water circulation and hot water circulation: cold water enters a first-stage evaporator 3-1 from a cold water inlet, enters a second-stage evaporator 3-2 after first heat release and temperature reduction, and flows out from a cold water outlet after further heat release and temperature reduction; hot water enters the first-stage condenser 4-1 from the hot water inlet, the temperature rises after heat absorption, and the hot water flows out from the hot water outlet.
(II) a refrigeration cycle system:
(1) a main circulation loop: the gaseous refrigerant outlet of the first-stage evaporator 3-1 is communicated with the air inlet of the compressor 1, the air outlet of the compressor 1 is communicated with the gaseous refrigerant inlet of the first-stage condenser 4-1, and the liquid refrigerant outlet of the first-stage condenser 4-1 is connected with the liquid refrigerant inlet of the first-stage evaporator 3-1 through a refrigerant throttling device 5 to form a main circulation loop.
(2) The auxiliary circulation branch of the evaporator: the liquid refrigerant outlet of the first-stage evaporator 3-1 is communicated with the liquid refrigerant inlet of the second-stage evaporator 3-2 through a throttling device 7-1 of the first-stage evaporator; the gas refrigerant outlet of the second-stage evaporator 3-2 is communicated with the gas inlet of the first low-temperature low-pressure-ratio compressor 2-1, the gas outlet of the first low-temperature low-pressure-ratio compressor 2-1 is communicated with the connecting pipeline of the gas refrigerant outlet of the first-stage evaporator 3-1 and the inlet of the compressor 1, or the gas outlet of the first-stage low-temperature low-pressure-ratio compressor 2-1 is communicated with the gas inlet of the first-stage evaporator 3-1;
(3) a refrigerant circulation mechanism: high-pressure refrigerant steam at an air outlet of the compressor 1 enters a first-stage condenser 4-1, forms liquid refrigerant after heat release and condensation, flows out of the first-stage condenser 4-1, enters a refrigerant throttling device 5, enters a first-stage evaporator 3-1 after throttling and pressure reduction to form two paths, one path of liquid refrigerant absorbs heat and evaporates to become gaseous refrigerant, the other path of liquid refrigerant further throttles and reduces pressure through a first-stage evaporator throttling device 7-1 and then enters a second-stage evaporator 3-2, absorbs heat and evaporates to become gaseous refrigerant, the gaseous refrigerant flowing out of the second-stage evaporator 3-2 enters a low-temperature low-pressure-ratio compressor 2-1 to be compressed, then is mixed with the gaseous refrigerant flowing out of the first-stage evaporator 3-1, then enters the compressor 1 to increase pressure, and refrigerant circulation is completed.
Preferably, the compressor 1 is a high pressure ratio compressor.
Furthermore, the working medium in the multistage series compression heat pump unit can be liquid water, air and antifreeze.
Further, the first low-temperature low-pressure-ratio compressor 2-1 and the compressor 1 are coaxially arranged, and the outer walls of the first low-temperature low-pressure-ratio compressor and the compressor 1 share a shell to form an integrated compressor with two-stage compression functions.
Preferably, the integrated compressor is an impeller compressor. Specifically, the compressor in the multistage tandem compression heat pump unit can adopt an axial flow compressor and/or a centrifugal compressor, or other compressors.
It is worth mentioning that the existing compressor is sequentially divided into a rotor compressor, a turbine compressor, a screw compressor, a centrifugal compressor and an axial compressor according to the power from small to large, wherein the rotor compressor and the turbine compressor are piston type compressors, and the centrifugal compressor and the axial compressor are impeller type compressors, and the impeller type compressors have the advantages of high efficiency, small volume and stable operation.
Specifically, the evaporator throttling device and the condenser throttling device may be expansion valves.
The heat pump unit is suitable for occasions with large temperature difference between the cold water inlet and the cold water outlet and small temperature difference between the hot water inlet and the hot water outlet.
Example 2: three-stage evaporation series compression heat pump unit
Embodiment 2 provides a three-stage evaporation series compression heat pump unit, and on the basis of the two-stage evaporation series compression heat pump unit provided in embodiment 1, as shown in fig. 2, embodiment 2 is additionally provided with a third-stage evaporator 3-3, a second-stage evaporator throttling device 7-2 and a second-stage low-temperature low-pressure ratio compressor 2-2.
Supply of cold and hot water
a. Cold water supply interface: the primary evaporator 3-1, the secondary evaporator 3-2 and the tertiary evaporator 3-3 are sequentially connected in series through pipelines from right to left, a water inlet of the primary evaporator 3-1 is used as a cold water inlet of the whole unit, and a water outlet of the tertiary evaporator 3-3 is used as a cold water outlet.
b. A hot water supply interface: the water inlet and the water outlet of the primary condenser 4-1 are used as a hot water inlet and a hot water outlet of the whole unit.
c. Cold water circulation and hot water circulation: cold water enters a first-stage evaporator 3-1 from a cold water inlet, enters a second-stage evaporator 3-2 after first heat release and temperature reduction, enters a third-stage evaporator 3-3 after heat release and temperature reduction, further releases heat and reduces temperature, and flows out from a cold water outlet; hot water enters the first-stage condenser 4-1 from the hot water inlet, the temperature rises after heat absorption, and the hot water flows out from the hot water outlet.
(II) a refrigeration cycle system:
(1) a main circulation loop: the same as example 1;
(2) the auxiliary circulation branch of the evaporator:
the liquid refrigerant outlet of the second-stage evaporator 3-2 is communicated with the liquid refrigerant inlet of the third-stage evaporator 3-3 through a throttling device 7-2 of the second-stage evaporator; a gas refrigerant outlet of the third-stage evaporator 3-3 is communicated with a gas inlet of the second-stage low-temperature low-pressure-ratio compressor 2-2, and a gas outlet of the second-stage low-temperature low-pressure-ratio compressor 2-2 is communicated with a gas refrigerant inlet of the second-stage evaporator 3-2;
the connection relationship among the second-stage evaporator 3-2, the first-stage evaporator 3-1, the first-stage condenser 4-1, the compressor 1, the first low-temperature low-pressure-ratio compressor 2-1, the refrigerant throttling device 5 and the first-stage evaporator throttling device 7-1 is shown in example 1.
(3) A refrigerant circulation mechanism: high-pressure refrigerant steam at an air outlet of the compressor 1 enters a first-stage condenser 4-1, heat is released and condensed into liquid refrigerant, the liquid refrigerant flows out of the first-stage condenser 4-1 and enters a refrigerant throttling device 5, the refrigerant is throttled and reduced in pressure and then enters a first-stage evaporator 3-1 and then is divided into two paths for the first time, one path of liquid refrigerant absorbs heat and is evaporated into gaseous refrigerant, the other path of liquid refrigerant further throttled and reduced in pressure by a first-stage evaporator throttling device 7-1 and then enters a second-stage evaporator 3-2 and then is divided into two paths again, one path of liquid refrigerant absorbs heat and is evaporated into gaseous refrigerant in a second-stage evaporator 3-2, the other path of liquid refrigerant further throttled and reduced in pressure by a second-stage evaporator throttling device 7-2 and then enters a third-stage evaporator 3-3 and is evaporated into gaseous refrigerant, the gaseous refrigerant flowing out of the third-stage evaporator 3 enters a second-stage low-temperature low-pressure ratio compressor 2 and is compressed and then is compressed Enters the second-stage evaporator 3-2, is mixed with the gaseous refrigerant evaporated in the second-stage evaporator 3-2, enters the first-stage low-temperature low-pressure-ratio compressor 2-1 together, is compressed, then enters the first-stage evaporator 3-1, is mixed with the gaseous refrigerant evaporated in the first-stage evaporator 3-1, and finally enters the compressor 1 together to boost the pressure, thereby completing the refrigerant circulation.
The heat pump unit is suitable for occasions with large temperature difference between the cold water inlet and the cold water outlet and small temperature difference between the hot water inlet and the hot water outlet.
Example 3: three-stage evaporation series compression type heat exchange unit with water-water heat exchanger
Embodiment 3 provides a three-stage evaporation series compression heat exchanger unit with a water-water heat exchanger, and as shown in fig. 3, a water-water heat exchanger 9 is additionally provided on the basis of the three-stage evaporation series compression heat exchanger unit of embodiment 2.
The connection relationship of the water-water heat exchanger 9 is as follows: the water-water heat exchanger 9, the primary evaporator 3-1, the secondary evaporator 3-2 and the tertiary evaporator 3-3 are sequentially connected in series through pipelines from left to right, a primary water outlet of the water-water heat exchanger 9 is communicated with a water inlet of the primary evaporator 3-1, a primary water inlet of the water-water heat exchanger 9 is used as a cold water inlet, namely a primary water inlet of the whole unit, and a primary water outlet of the water-water heat exchanger 9 is used as a cold water outlet; the hot water side of the first-stage condenser 4-1 and the secondary water side of the water-water heat exchanger 9 are connected in parallel between the secondary water inlet and the secondary water outlet, the secondary water inlet is used as a hot water inlet, and the secondary water outlet is used as a hot water outlet. Specifically, a hot water inlet of the primary condenser 4-1 and a secondary water inlet of the water-water heat exchanger 9 are communicated to the secondary water inlet together, and a hot water outlet of the primary condenser 4-1 and a secondary water outlet of the water-water heat exchanger 9 are communicated to the secondary water outlet together. See example 2 for the remaining structural connections.
A refrigerant circulation mechanism: see example 2.
In embodiment 5, the secondary water returned from the heat consumer is divided into two paths, one path enters the first-stage condenser 4-1 to absorb heat and raise temperature; the other path enters a water-water heat exchanger 9 to absorb heat and raise temperature, and the two paths of water are converged and then are conveyed to a heat user;
the primary water from the heat source plant firstly enters the water-water heat exchanger 9 for heat release and temperature reduction, then enters the primary evaporator 3-1 for heat release and temperature reduction, then enters the secondary evaporator 3-2 for further heat release and temperature reduction, and finally enters the tertiary evaporator 3-3 for further heat release and temperature reduction and then returns to the heat source plant.
The compression type heat exchange unit is suitable for the heat exchange process of primary water and secondary water in a central heating system heating station.
Example 4: two-stage condensation series compression heat pump unit
Embodiment 4 provides a two-stage condensation tandem compression heat pump unit, as shown in fig. 4, the heat pump unit includes a first-stage evaporator 3-1, a compressor 1, a first-stage high-temperature low-pressure ratio compressor 8-1, a refrigerant throttling device 5, a first-stage condenser throttling device 6-1, a first-stage condenser 4-1, and a second-stage condenser 4-2.
Supply of cold and hot water
a. Cold water supply interface: the cold water inlet and the cold water outlet are respectively and directly communicated with the water inlet and the water outlet of the primary evaporator 3-1 or the water inlet and the water outlet of the primary evaporator 3-1 are used as the cold water inlet and the cold water outlet of the whole unit.
b. A hot water supply interface: the first-stage condenser 4-1 and the second-stage condenser 4-2 are connected in series, specifically, a hot water inlet is communicated with a water inlet of the first-stage condenser 4-1 or a water inlet of the first-stage condenser 4-1 is used as a hot water inlet of the whole unit, a water outlet of the second-stage condenser 4-2 is used as a hot water outlet of the whole unit, and a water outlet of the first-stage condenser 4-1 is connected with a water inlet of the second-stage condenser 4-2 through a pipeline.
c. Cold water circulation and hot water circulation: cold water enters the primary evaporator 3-1 from a cold water inlet, the temperature is reduced after heat release, and the cold water flows out from a cold water outlet; hot water enters the first-stage condenser 4-1 from a hot water inlet, enters the second-stage condenser 4-2 after first heat absorption and temperature rise, and flows out from a hot water outlet after further heat absorption and temperature rise.
(II) a refrigeration cycle system:
(1) a main circulation loop: the same as in example 1.
(2) A condenser auxiliary circulation branch: a gas refrigerant inlet of the second-stage condenser 4-2 is communicated with a gas outlet of the first-stage high-temperature low-pressure-ratio compressor 8-1, a gas inlet of the first-stage high-temperature low-pressure-ratio compressor 8-1 is communicated with the main circulation loop, and specifically, the gas inlet of the first-stage high-temperature low-pressure-ratio compressor 8-1 is communicated with a connecting pipeline of the gas refrigerant inlet of the first-stage condenser 4-1 and the gas outlet of the compressor 1 or is directly communicated with a gas refrigerant outlet of the first-stage condenser 4-1; the liquid refrigerant outlet of the second-stage condenser 4-2 is communicated with the liquid refrigerant inlet of the first-stage condenser 4-1 through the first-stage condenser throttling device 6-1, specifically, the liquid refrigerant outlet of the second-stage condenser 4-2 is communicated with the liquid refrigerant inlet of the first-stage condenser throttling device 6-1, and the liquid refrigerant outlet of the first-stage condenser throttling device 6-1 is communicated with the liquid refrigerant inlet of the first-stage condenser 4-1.
(3) A refrigerant circulation mechanism: high-pressure refrigerant steam at the outlet of the compressor 1 is divided into two paths, one path of the high-pressure refrigerant steam enters the first-stage condenser 4-1 to release heat and condense into liquid refrigerant, the other path of the high-pressure refrigerant steam enters the first-stage condenser 4-1 to release heat and condense into liquid refrigerant after entering the first-stage condenser 4-2 after further boosting the pressure of the first-stage high-temperature low-pressure ratio compressor 8-1, the liquid refrigerant at the outlet of the second-stage condenser 4-2 enters the first-stage condenser 4-1 to further release heat and cool after throttling and reducing the pressure of the first-stage condenser 6-1, the converged liquid refrigerant flows out of the first-stage condenser 4-1 to enter the refrigerant throttling device 5, and enters the first-stage evaporator 3-1 after throttling and reducing the pressure, the heat absorption evaporation is changed into gaseous refrigerant, and then the refrigerant enters the compressor 1 to boost the pressure, and complete the refrigerant circulation.
The heat pump unit is suitable for occasions with large temperature difference of the hot water side inlet and the hot water side outlet and small temperature difference of the cold water side inlet and the cold water side outlet.
Example 5: three-stage condensation series compression heat pump unit
Embodiment 5 provides a three-stage condensation tandem compression heat pump unit, and on the basis of the two-stage condensation tandem compression heat pump unit provided in embodiment 4, as shown in fig. 5, the heat pump unit further includes a second-stage high-temperature low-pressure-ratio compressor 8-2, a second condenser throttling device 6-2, and a third-stage condenser 4-3.
a. Cold water supply interface: the water inlet and the water outlet of the primary evaporator 3-1 are used as a cold water inlet and a cold water outlet of the whole unit.
b. A hot water supply interface: the first-stage condenser 4-1, the second-stage condenser 4-2 and the third-stage condenser 4-3 are sequentially connected in series through pipelines from right to left, a water inlet of the first-stage condenser 4-1 is used as a hot water inlet of the whole unit, and a water outlet of the third-stage condenser 4-3 is used as a hot water outlet of the whole unit.
c. Cold water circulation and hot water circulation: cold water enters the primary evaporator 3-1 from a cold water inlet, the temperature is reduced after heat release, and the cold water flows out from a cold water outlet; hot water enters the first-stage condenser 4-1 from a hot water inlet, enters the second-stage condenser 4-2 after first heat absorption and temperature rise, enters the third-stage condenser 4-3 after second heat absorption and temperature rise, further absorbs heat and rises temperature, and then flows out from a hot water outlet.
(II) a refrigeration cycle system:
(1) a main circulation loop: the same as in example 1.
(2) A condenser auxiliary circulation branch:
a gas refrigerant outlet of the second-stage condenser 4-2 is communicated with a gas inlet of the second-stage high-temperature low-pressure ratio compressor 8-2, and a gas outlet of the second-stage high-temperature low-pressure ratio compressor 8-2 is communicated with a gas refrigerant inlet of the third-stage condenser 4-3; the liquid refrigerant outlet of the third-stage condenser 4-3 is communicated with the liquid refrigerant inlet of the second-stage condenser 4-2 through a second condenser throttling device 6-2; see example 4 for the connection of the remaining structures.
(3) A refrigerant circulation mechanism: high-pressure refrigerant steam at the outlet of the compressor 1 enters a first-stage condenser 4-1 and then is divided into two paths for the first time, one path releases heat and is condensed into liquid refrigerant, the other path enters a first-stage high-temperature low-pressure ratio compressor 8-1 for further pressure rise and then enters a second-stage condenser 4-2 and then is divided into two paths again, one path releases heat and is condensed into liquid refrigerant in the second-stage condenser 4-2, the other path enters a second-stage high-temperature low-pressure ratio compressor 8-2 for further pressure rise and then enters a third-stage condenser 4-3 for releasing heat and being condensed into liquid refrigerant; the liquid refrigerant at the outlet of the third-stage condenser 4-3 is throttled and depressurized by a second condenser throttling device 6-2, enters a second-stage condenser 4-2 for further heat release and temperature reduction, is throttled and depressurized by a first-stage condenser throttling device 6-1 together with the liquid refrigerant condensed in the second-stage condenser 4-2, and then enters a first-stage condenser 4-1 for further heat release and temperature reduction; the liquid refrigerant condensed in the first-stage condenser 4-1 is gathered and flows out of the first-stage condenser 4-1 to enter a refrigerant throttling device 5, enters a first evaporator 3-1 after throttling and pressure reduction, absorbs heat and evaporates to become a gaseous refrigerant, and then enters a compressor 1 to increase the pressure, so that the refrigerant circulation is completed.
The heat pump unit is suitable for occasions with large temperature difference between the hot water side inlet and the hot water side outlet and small temperature difference between the cold water side inlet and the cold water side outlet.
Example 6: three-stage evaporation and three-stage condensation series compression heat pump unit
Embodiment 6 provides a three-stage evaporation and three-stage condensation tandem compression heat pump unit, as shown in fig. 6, the heat pump unit includes a first-stage evaporator 3-1, a second-stage evaporator 3-2, a third-stage evaporator 3-3, a compressor 1, a refrigerant throttling device 5, a first-stage low-temperature low-pressure ratio compressor 2-1, a second-stage low-temperature low-pressure ratio compressor 2-2, a first-stage evaporator throttling device 7-1, a second-stage evaporator throttling device 7-2, a first-stage high-temperature low-pressure ratio compressor 8-1, a second-stage high-temperature low-pressure ratio compressor 8-2, a first-stage condenser throttling device 6-1, a second-condenser throttling device 6-2, a first-stage condenser 4-1, a second-stage condenser 4-2, and a third-stage condenser 4-3.
a. Cold water supply interface: the primary evaporator 3-1, the secondary evaporator 3-2 and the tertiary evaporator 3-3 are sequentially connected in series through pipelines from right to left, a water inlet of the primary evaporator 3-1 is used as a cold water inlet of the whole unit, and a water outlet of the tertiary evaporator 3-3 is used as a cold water outlet.
b. A hot water supply interface: the first-stage condenser 4-1, the second-stage condenser 4-2 and the third-stage condenser 4-3 are sequentially connected in series through pipelines from right to left, a water inlet of the first-stage condenser 4-1 is used as a hot water inlet of the whole unit, and a water outlet of the third-stage condenser 4-3 is used as a hot water outlet.
c. Cold water circulation and hot water circulation: hot water enters a first-stage condenser 4-1 from a hot water inlet, enters a second-stage condenser 4-2 after first heat absorption and temperature rise, enters a third-stage condenser 4-3 after second heat absorption and temperature rise, further absorbs heat and rises temperature, and then flows out from a hot water outlet; cold water firstly enters the first-stage evaporator 3-1 from a cold water inlet, enters the second-stage evaporator 3-2 after first heat release and temperature reduction, enters the third-stage evaporator 3-3 after heat release and temperature reduction, further releases heat and reduces temperature, and flows out from a cold water outlet.
(II) a refrigeration cycle system:
(1) a main circulation loop: the same as in example 1.
(2) The auxiliary circulation branch of the evaporator: the outlet of the second-stage evaporator 3-2 gaseous refrigerant is connected with the inlet of the first-stage low-temperature low-pressure-ratio compressor 2-1, and the outlet of the first-stage low-temperature low-pressure-ratio compressor 2-1 is connected to a connecting pipe between the outlet of the first-stage evaporator 3-1 gaseous refrigerant and the inlet of the compressor 1;
a gaseous refrigerant outlet of the third-stage evaporator 3-3 is connected with an inlet of the second-stage low-temperature low-pressure-ratio compressor 2-2, and an outlet of the second-stage low-temperature low-pressure-ratio compressor 2-2 is connected to a connecting pipeline between the gaseous refrigerant outlet of the second-stage evaporator 3-2 and the inlet of the first-stage low-temperature low-pressure-ratio compressor 2-1;
the liquid refrigerant outlet of the first-stage evaporator 3-1 is communicated to the liquid refrigerant inlet of the second-stage evaporator 3-2 through the first-stage evaporator throttling device 7-1, and the liquid refrigerant outlet of the second-stage evaporator 3-2 is communicated to the liquid refrigerant inlet of the third-stage evaporator 3-3 through the second-stage evaporator throttling device 7-2.
(3) A condenser auxiliary circulation branch:
an inlet of the first-stage high-temperature low-pressure ratio compressor 8-1 is connected to a connecting pipeline between an inlet of a gaseous refrigerant of the first-stage condenser 4-1 and an outlet of the compressor 1, and an outlet of the first-stage high-temperature low-pressure ratio compressor 8-1 is connected with an inlet of a gaseous refrigerant of the second-stage condenser 4-2;
the inlet of the second-stage high-temperature low-pressure ratio compressor 8-2 is connected to a connecting pipeline between the gaseous refrigerant inlet of the second-stage condenser 4-2 and the outlet of the first-stage high-temperature low-pressure ratio compressor 8-1, and the outlet of the second-stage high-temperature low-pressure ratio compressor 8-2 is connected with the gaseous refrigerant inlet of the third-stage condenser 4-3;
the liquid refrigerant outlet of the third-stage condenser 4-3 is connected to the liquid refrigerant inlet of the second-stage condenser 4-2 through a second throttling device 6-2, and the liquid refrigerant outlet of the second-stage condenser 4-2 is connected with the liquid refrigerant inlet of the first-stage condenser 4-1 through a first-stage condenser throttling device 6-1.
A refrigerant circulation mechanism: high-pressure refrigerant steam at the air outlet of the compressor 1 is divided into two paths, one path of the high-pressure refrigerant steam enters the first-stage condenser 4-1 and then releases heat to be condensed into liquid refrigerant, the other path of the high-pressure refrigerant steam enters the first-stage high-temperature low-pressure ratio compressor 8-1 and then is divided into two paths of the high-pressure refrigerant steam after being further boosted, one path of the high-pressure refrigerant steam releases heat to be condensed into liquid refrigerant in the second-stage condenser 4-2, and the other path of the high-pressure refrigerant steam enters the second-stage high-temperature low-pressure ratio compressor 8-2 and then enters the third-stage condenser 4-3 after being further boosted, and the heat is released and condensed into liquid refrigerant; the liquid refrigerant at the outlet of the third-stage condenser 4-3 is throttled and decompressed by the second throttling device 6-2, enters the second-stage condenser 4-2 for further heat release and temperature reduction, then enters the first-stage condenser 4-1 for further heat release and temperature reduction after being throttled and decompressed by the first-stage condenser throttling device 6-1 together with the liquid refrigerant condensed in the second-stage condenser 4-2, is gathered with the liquid refrigerant condensed in the first-stage condenser 4-1 and flows out of the first-stage condenser 4-1 to enter the refrigerant throttling device 5, enters the first-stage evaporator 3-1 after being throttled and decompressed, one part of the liquid refrigerant absorbs heat and is evaporated into a gaseous refrigerant, the other part of the liquid refrigerant is further throttled and decompressed by the first-stage evaporator throttling device 7-1 and enters the second-stage evaporator 3-2, and then the refrigerant is divided into two paths, wherein one path is subjected to heat absorption evaporation in the second-stage evaporator 3-2 to become gaseous refrigerant, the other path is subjected to further throttling and pressure reduction through the second-stage evaporator throttling device 7-2 and then enters the third-stage evaporator 3-3 to be subjected to heat absorption evaporation to become gaseous refrigerant, the gaseous refrigerant flowing out of the third-stage evaporator 3-3 enters the second-stage low-temperature low-pressure-ratio compressor 2-2 to be compressed and then is mixed with the gaseous refrigerant evaporated in the second-stage evaporator 3-2, and then enters the first-stage low-temperature low-pressure-ratio compressor 2-1 to be compressed and then is mixed with the gaseous refrigerant evaporated in the first-stage evaporator 3-1, and finally enters the compressor 1 to be pressurized, so that the circulation is completed. The hot water firstly enters a first-stage condenser 4-1 for heat absorption and temperature rise, then enters a second-stage condenser 4-2 for further heat absorption and temperature rise, and finally enters a third-stage condenser 4-3 for further heat absorption and temperature rise; the cold water firstly enters the first-stage evaporator 3-1 for heat release and temperature reduction, then enters the second-stage evaporator 3-2 for further heat release and temperature reduction, and finally enters the third-stage evaporator 3-3 for further heat release and temperature reduction.
The heat pump unit is suitable for occasions with large temperature difference between the hot water side and the cold water side and the outlet.
In the above embodiments, embodiment 1, embodiment 2, and embodiment 3 are suitable for the case when the cold water side has a large temperature difference and a small flow rate; examples 4 and 5 are suitable for the situation when the hot water side has a large temperature difference and a small flow rate; embodiment 6 is suitable for a situation when both the cold water side and the hot water side have a large temperature difference and a small flow rate.
The above embodiments are only used for further detailed description of the object, technical solution and beneficial effect of the present invention, and are not used for limiting the present invention. The scope of the present invention includes, but is not limited to, the above embodiments, and any modifications, substitutions, variations, improvements, etc. which may occur to those skilled in the art, within the spirit and principle of the present invention, are intended to be included within the scope of the present invention.

Claims (5)

1. A multistage series compression heat pump unit is characterized in that the multistage series compression heat pump unit comprises a multistage condenser, a multistage evaporator, a refrigerant throttling device (5), a compressor (1) and at least one stage of evaporator throttling device, wherein at least one stage of low-temperature low-pressure-ratio compressor and at least one stage of condenser throttling device are arranged, and at least one stage of high-temperature low-pressure-ratio compressor is arranged,
the condenser is a multistage condenser (4-1, 4-2, …, 4-n), a hot water inlet is arranged at a water inlet of the first-stage condenser (4-1), the multistage condensers (4-1, 4-2, …, 4-n) are sequentially connected in series from a hot water inflow end to a hot water outflow end, and a hot water outlet is arranged at a water outlet of the last-stage condenser (4-n);
the evaporator is a multi-stage evaporator (3-1, 3-2, …, 3-m), a cold water inlet is arranged at a water inlet of the first-stage evaporator (3-1), the multi-stage evaporators (3-1, 3-2, …, 3-m) are sequentially connected in series from a cold water inflow end to a cold water outflow end, and a cold water outlet is arranged at a water outlet of the last-stage evaporator (3-m);
the gas refrigerant outlet of the primary evaporator (3-1) is communicated with the air inlet of the compressor (1), the air outlet of the compressor (1) is communicated with the gas refrigerant inlet of the primary condenser (4-1), and the liquid refrigerant outlet of the primary condenser (4-1) is connected with the liquid refrigerant inlet of the primary evaporator (3-1) through the refrigerant throttling device (5), so that a main circulation loop is formed;
the multistage series compression heat pump unit also comprises at least one stage of evaporator auxiliary circulation branch and at least one stage of condenser auxiliary circulation branch which are communicated with the main circulation loop;
each stage of evaporator auxiliary circulation branch is provided with at least one low-temperature low-pressure ratio compressor and at least one evaporator throttling device, and the condenser auxiliary circulation branch is provided with at least one condenser throttling device and at least one high-temperature low-pressure ratio compressor;
a first-stage evaporator throttling device (7-1), a low-temperature low-pressure-ratio compressor (2-1) and a second-stage evaporator (3-2) are arranged on the auxiliary circulation branch of the first-stage evaporator, and a liquid refrigerant inlet of the second-stage evaporator (3-2) is communicated with a liquid refrigerant outlet of the first-stage evaporator (3-1) through the first-stage evaporator throttling device (7-1); the gaseous refrigerant outlet of the second-stage evaporator (3-2) is communicated with the main circulation loop through the low-temperature low-pressure-ratio compressor (2-1);
the liquid refrigerant inlet of the ith stage evaporator (3-i) is communicated with the liquid refrigerant outlet of the ith-1 stage evaporator (3- (i-1)) or the liquid refrigerant outlet of the first stage condenser (4-1) through the ith stage evaporator throttling device (7-i);
the gaseous refrigerant outlet of the (i + 1) th stage evaporator (3- (i + 1)) is communicated with the gaseous refrigerant inlet of the (i) th stage evaporator (3-i) through the (i) th stage low-temperature low-pressure ratio compressor (2-i) or the gaseous refrigerant outlet of the (i) th stage evaporator (3-i) is communicated with the connecting pipe of the air inlet of the (i-1) th stage low-temperature low-pressure ratio compressor (2- (i-1));
a first-stage condenser throttling device (6-1), a first-stage high-temperature low-pressure-ratio compressor (8-1) and a second-stage condenser (4-2) are arranged on the first-stage condenser auxiliary circulation branch, and a gas refrigerant inlet of the second-stage condenser (4-2) is communicated with the gas refrigerant inlet of the first-stage condenser (4-1) or a gas refrigerant outlet of the first-stage condenser (4-1) through the first-stage high-temperature low-pressure-ratio compressor (8-1); the liquid refrigerant outlet of the second-stage condenser (4-2) is communicated with the main circulation loop through a first-stage condenser throttling device (6-1);
a j-th-stage condenser throttling device (6-j), a j-th-stage high-temperature low-pressure-ratio compressor (8-j) and a j + 1-th-stage condenser (4- (j + 1)) are arranged on the j-th-stage condenser auxiliary circulation branch, and a j + 1-th-stage condenser (4- (j + 1)) gaseous refrigerant inlet is communicated with a j-th-stage condenser (4-j) gaseous refrigerant outlet through the j-th-stage high-temperature low-pressure-ratio compressor (8-j); the liquid refrigerant outlet of the j +1 th-stage condenser (4- (j + 1)) is communicated with the liquid refrigerant inlet of the j-th-stage condenser (4-j) through a j-th-stage condenser throttling device (6-j) or the liquid refrigerant outlet of the j-th-stage condenser (4-j) is communicated with the liquid refrigerant inlet connecting pipe of the j-1 th-stage condenser throttling device (6- (j-1)) or the liquid refrigerant inlet of the first-stage condenser.
2. The multistage series compression heat pump unit of claim 1, wherein the multistage series compression heat pump unit comprises a water-water heat exchanger (9),
a primary water outlet of the water-water heat exchanger (9) is communicated with a water inlet of the primary evaporator (3-1), a primary water inlet of the water-water heat exchanger (9) is used as a primary water inlet of the whole unit, and a water outlet of the last-stage evaporator is used as a primary water outlet of the whole unit;
the hot water side inlet of the first-stage condenser (4-1) is connected with the secondary water side inlet of the water-water heat exchanger (9) in parallel to serve as a secondary water inlet of the whole unit, and the hot water side outlet of the last-stage condenser is connected with the secondary water side outlet of the water-water heat exchanger (9) in parallel to serve as a secondary water outlet of the whole unit.
3. The multi-stage tandem compression heat pump unit of claim 1,
the compressor (1) is a high pressure ratio compressor.
4. The multistage series compression heat pump unit according to any one of claims 1 to 2,
the multistage low-temperature low-pressure-ratio compressor is coaxially arranged and the outside of the low-temperature low-pressure-ratio compressor shares the same shell to form an integrated compressor with a multistage compression function.
5. The multi-stage tandem compression heat pump unit of claim 4,
the integrated compressor is an impeller compressor.
CN201910159962.4A 2019-03-04 2019-03-04 Multistage series compression heat pump unit Active CN109708337B (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
CN201910159962.4A CN109708337B (en) 2019-03-04 2019-03-04 Multistage series compression heat pump unit

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
CN201910159962.4A CN109708337B (en) 2019-03-04 2019-03-04 Multistage series compression heat pump unit

Publications (2)

Publication Number Publication Date
CN109708337A CN109708337A (en) 2019-05-03
CN109708337B true CN109708337B (en) 2021-10-01

Family

ID=66265579

Family Applications (1)

Application Number Title Priority Date Filing Date
CN201910159962.4A Active CN109708337B (en) 2019-03-04 2019-03-04 Multistage series compression heat pump unit

Country Status (1)

Country Link
CN (1) CN109708337B (en)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN112378081A (en) * 2020-12-03 2021-02-19 宁波蓝释电子科技有限公司 Air energy water heater system and control method

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN101093116A (en) * 2007-05-25 2007-12-26 清华大学 Multistage-cascaded compression type heat pump set under large temperature difference
CN102445016A (en) * 2011-11-16 2012-05-09 广州市设计院 Method for preparing large-temperature difference chilled water in single machine two-stage compression manner and special water chilling unit
CN103925726A (en) * 2014-04-29 2014-07-16 挪信能源技术(上海)有限公司 Embedded type high-temperature heat pump unit
CN106403282A (en) * 2016-11-17 2017-02-15 珠海格力电器股份有限公司 Heat pump hot water system and heat pump water heater with heat pump hot water system
JP2017227421A (en) * 2016-06-24 2017-12-28 株式会社デンソー Heat pump device
US20180187927A1 (en) * 2017-01-03 2018-07-05 Heatcraft Refrigeration Products Llc System and method for reusing waste heat of a transcritical refrigeration system

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP5346343B2 (en) * 2008-08-27 2013-11-20 株式会社前川製作所 Two-stage compression heat pump cycle device
CN104807184B (en) * 2015-04-27 2017-07-14 西安交通大学 A kind of two stages of compression heat pump water heater system and its method of work

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN101093116A (en) * 2007-05-25 2007-12-26 清华大学 Multistage-cascaded compression type heat pump set under large temperature difference
CN102445016A (en) * 2011-11-16 2012-05-09 广州市设计院 Method for preparing large-temperature difference chilled water in single machine two-stage compression manner and special water chilling unit
CN103925726A (en) * 2014-04-29 2014-07-16 挪信能源技术(上海)有限公司 Embedded type high-temperature heat pump unit
JP2017227421A (en) * 2016-06-24 2017-12-28 株式会社デンソー Heat pump device
CN106403282A (en) * 2016-11-17 2017-02-15 珠海格力电器股份有限公司 Heat pump hot water system and heat pump water heater with heat pump hot water system
US20180187927A1 (en) * 2017-01-03 2018-07-05 Heatcraft Refrigeration Products Llc System and method for reusing waste heat of a transcritical refrigeration system

Also Published As

Publication number Publication date
CN109708337A (en) 2019-05-03

Similar Documents

Publication Publication Date Title
CN201037719Y (en) Hot-water heat pump set for gradual increasing water temperature
EP2147265B8 (en) Refrigerating device and method for circulating a refrigerating fluid associated with it
CN100491866C (en) Multistage-cascaded compression type heat pump set under large temperature difference
CN109736909A (en) The compressed-air energy-storage system of multipotency alliance
CN107366621B (en) Rolling rotor compressor with three-stage air supplement and air conditioning system
CN100501267C (en) Plural serial stage waterway single heating type heat pump water heating machine
CN109708337B (en) Multistage series compression heat pump unit
CN204141879U (en) Heat pump
CN112325510A (en) Circulating cooling water temperature-distribution device suitable for large-scale power plant
CN101487643A (en) Ultra-low temperature heat pump air conditioning system
CN108759143A (en) A kind of special cascade superhigh temperature hot water air source heat pump system
CN211119989U (en) Multi-stage compression multi-condenser intermediate throttling incomplete cooling medium-high temperature heat pump system
CN110173913A (en) A kind of steam compressed high temperature heat pump unit of very large super cooling degree
CN214620159U (en) Multi-stage refrigerating unit
CN217110104U (en) Vapor compression type refrigeration heat pump circulating system with surrounding type heat regenerator
CN111141135B (en) Multistage waste heat recovery and free heat distribution air source hot air drying system and heat distribution method
CN110307673B (en) Solar energy synergistic heat pump system
CN210004626U (en) ground source heat pump heat recovery unit with high-efficiency throttling system
CN213335032U (en) Refrigerating system
CN110748937B (en) Compressor double-pressure working condition large-temperature-difference heat taking electric drive heat pump unit and working method
CN217785518U (en) Air source heat pump unit
WO2022116133A1 (en) Wide-range low-temperature refrigeration system for test chamber
CN202032780U (en) Hydrojet reinforcement condensation refrigeration system
CN209484880U (en) One kind is risen again formula heat pump system
CN108036445B (en) Improved heat source tower heat pump device

Legal Events

Date Code Title Description
PB01 Publication
PB01 Publication
SE01 Entry into force of request for substantive examination
SE01 Entry into force of request for substantive examination
GR01 Patent grant
GR01 Patent grant