CN104713264A - Air source heat pump set - Google Patents
Air source heat pump set Download PDFInfo
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- CN104713264A CN104713264A CN201310675422.4A CN201310675422A CN104713264A CN 104713264 A CN104713264 A CN 104713264A CN 201310675422 A CN201310675422 A CN 201310675422A CN 104713264 A CN104713264 A CN 104713264A
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- valve
- valve port
- heat exchanger
- air
- heat pump
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- 238000005057 refrigeration Methods 0.000 claims abstract description 35
- 239000011552 falling film Substances 0.000 claims abstract description 24
- 238000010438 heat treatment Methods 0.000 claims abstract description 14
- 230000008676 import Effects 0.000 claims description 4
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 abstract description 13
- 239000003507 refrigerant Substances 0.000 description 62
- 239000007788 liquid Substances 0.000 description 18
- 239000002826 coolant Substances 0.000 description 16
- 238000001704 evaporation Methods 0.000 description 9
- 238000010257 thawing Methods 0.000 description 9
- 238000007599 discharging Methods 0.000 description 8
- 230000008020 evaporation Effects 0.000 description 8
- 230000001105 regulatory effect Effects 0.000 description 8
- 238000010586 diagram Methods 0.000 description 7
- 238000012423 maintenance Methods 0.000 description 4
- 238000000034 method Methods 0.000 description 4
- 230000008569 process Effects 0.000 description 4
- 238000007493 shaping process Methods 0.000 description 4
- 230000008859 change Effects 0.000 description 3
- 230000007423 decrease Effects 0.000 description 3
- 230000008901 benefit Effects 0.000 description 2
- 230000001351 cycling effect Effects 0.000 description 2
- 239000012530 fluid Substances 0.000 description 2
- 239000000463 material Substances 0.000 description 2
- 238000012512 characterization method Methods 0.000 description 1
- 230000006835 compression Effects 0.000 description 1
- 238000007906 compression Methods 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 238000009434 installation Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000010355 oscillation Effects 0.000 description 1
- 238000012163 sequencing technique Methods 0.000 description 1
- 239000002699 waste material Substances 0.000 description 1
Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B29/00—Combined heating and refrigeration systems, e.g. operating alternately or simultaneously
- F25B29/003—Combined heating and refrigeration systems, e.g. operating alternately or simultaneously of the compression type system
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B41/00—Fluid-circulation arrangements
- F25B41/20—Disposition of valves, e.g. of on-off valves or flow control valves
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B41/00—Fluid-circulation arrangements
- F25B41/30—Expansion means; Dispositions thereof
- F25B41/31—Expansion valves
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B41/00—Fluid-circulation arrangements
- F25B41/30—Expansion means; Dispositions thereof
- F25B41/31—Expansion valves
- F25B41/34—Expansion valves with the valve member being actuated by electric means, e.g. by piezoelectric actuators
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
- F25B2400/19—Pumping down refrigerant from one part of the cycle to another part of the cycle, e.g. when the cycle is changed from cooling to heating, or before a defrost cycle is started
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2500/00—Problems to be solved
- F25B2500/06—Damage
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02B—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO BUILDINGS, e.g. HOUSING, HOUSE APPLIANCES OR RELATED END-USER APPLICATIONS
- Y02B30/00—Energy efficient heating, ventilation or air conditioning [HVAC]
- Y02B30/70—Efficient control or regulation technologies, e.g. for control of refrigerant flow, motor or heating
Landscapes
- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Mechanical Engineering (AREA)
- Thermal Sciences (AREA)
- General Engineering & Computer Science (AREA)
- Heat-Pump Type And Storage Water Heaters (AREA)
Abstract
The invention discloses an air source heat pump set. The air source heat pump set comprises a compressor, a four-way reverse valve, multiple fin heat exchangers, multiple four-way valves, a shell and tube heat exchanger, a falling film heat exchanger, a refrigeration throttling element and a refrigeration one-way valve. Each of the four-way valves comprises fifth to eighth valve ports; the fifth valve ports are connected with an exhaust port; the sixth valve ports are connected with the fin heat exchangers; the seventh valve ports are connected with third valve ports; the eighth valve ports are connected with the third valve ports through first throttling elements; each of the fin heat exchangers is provided with a one-way valve and a heating throttling element; and an outlet of each of the one-way valves is connected with each of the heating throttling elements through a public pipeline. The shell and tube heat exchanger is connected with the public pipeline through a check valve and a control valve. The falling film heat exchanger is connected with an air sucking port and the shell and tube heat exchanger. The air source heat pump set uninterruptedly and synchronously supplies cold sources and hot sources or living hot water to user sides so as to improve the use comfort of users.
Description
Technical field
The present invention relates to refrigerating field, especially relate to a kind of net for air-source heat pump units.
Background technology
Existing net for air-source heat pump units can not provide low-temperature receiver and thermal source simultaneously, and all needs unwanted cold or heat to be discharged in air when providing low-temperature receiver and thermal source demand, causes waste, makes the efficiency of net for air-source heat pump units low.And during providing thermal source in the winter time, need to defrost to finned heat exchanger, need cross valve to carry out commutating to transfer to refrigeration mode in defrost process, the refrigerant changed in finned heat exchanger flows to carry out reverse cycle defrosting.Because refrigerant pressure oscillation is impacted compressor comparatively large in reverse cycle defrosting process, the service life of compressor can be shortened, simultaneously in reverse cycle defrosting process, use side heat source temperature periodically sharply decline and cause comfortableness to reduce.
Summary of the invention
The present invention is intended at least to solve one of technical problem existed in prior art.For this reason, one object of the present invention is to propose a kind of net for air-source heat pump units, uninterruptedly can provide low-temperature receiver and thermal source or domestic hot-water to use side simultaneously.
According to the net for air-source heat pump units of the embodiment of the present invention, comprising: compressor, described compressor has exhaust outlet and air entry, four-way change-over valve, described four-way change-over valve has first to fourth valve port, and described first valve port is connected with described exhaust outlet, and described second valve port is connected with described air entry, multiple finned heat exchanger and multiple cross valve, described multiple finned heat exchanger and described multiple cross valve one_to_one corresponding, each described cross valve comprises the 5th to the 8th valve port, described 5th valve port of each described cross valve is connected with described exhaust outlet, described 6th valve port of each described cross valve is connected with one end of corresponding described finned heat exchanger, described 7th valve port of each described cross valve is connected with described 3rd valve port, described 8th valve port of each described cross valve is connected with described 3rd valve port by first throttle element, the other end of each described finned heat exchanger is provided with a check valve and heats restricting element, the outlet of each described check valve with each described in heat restricting element and be connected by common line, shell and tube exchanger, one end of described shell and tube exchanger is connected with described 4th valve port, and the other end of described shell and tube exchanger is connected with described common line with control valve by check-valves, falling-film heat exchanger, described falling-film heat exchanger has first mouth of pipe and second mouth of pipe, and described first mouth of pipe is connected with described air entry, and described second mouth of pipe is connected with the other end of described shell and tube exchanger, refrigeration restricting element, described refrigeration restricting element is connected with described second mouth of pipe, refrigeration check valve, the import of described refrigeration check valve is connected with described common line and exports and is connected with described refrigeration restricting element.
According to the net for air-source heat pump units of the embodiment of the present invention, by being provided with multiple finned heat exchanger, multiple cross valve, shell and tube exchanger and falling-film heat exchanger, thus low-temperature receiver and thermal source or domestic hot-water not only can be uninterruptedly provided to use side simultaneously, low-temperature receiver and thermal source are all utilized, improve the efficiency of net for air-source heat pump units, also can carry out the utilization of single low-temperature receiver or thermal source simultaneously, and can by providing the pattern seamless switching of low-temperature receiver and thermal source for providing the pattern of single low-temperature receiver or thermal source simultaneously.And uninterruptedly provide thermal source when can defrost to finned heat exchanger in the winter time according to the net for air-source heat pump units of the embodiment of the present invention, avoid traditional Temperature cycling sharply decline in use side of causing because finned heat exchanger defrosting and the comfortableness brought reduces, improve the comfort of user, and heating operation is continual and steady during defrosting, system pressure is not caused to change, therefore compressor is not impacted, extend the service life of compressor.
In addition, according to net for air-source heat pump units of the present invention, also there is following additional technical feature:
In some embodiments of the invention, described 5th valve port of described multiple cross valve is communicated with by first passage, and described first passage is connected with described exhaust outlet.Thus make the structure of net for air-source heat pump units simple.
According to some embodiments of the present invention, described 7th valve port of described multiple cross valve is communicated with by second channel, and described 3rd valve port is connected with described second channel.Thus make the structure of net for air-source heat pump units simple.
Further, described 8th valve port of each described cross valve is connected to described second channel by first throttle element.
Alternatively, described control valve is magnetic valve.
Alternatively, described refrigeration restricting element is electric expansion valve.
Alternatively, heating restricting element described in each is electric expansion valve or heating power expansion valve.
Particularly, described compressor is closed or semi-hermetic refrigerating compressor unit.
Alternatively, described compressor is helical-lobe compressor.
Additional aspect of the present invention and advantage will part provide in the following description, and part will become obvious from the following description, or be recognized by practice of the present invention.
Accompanying drawing explanation
Above-mentioned and/or additional aspect of the present invention and advantage will become obvious and easy understand from accompanying drawing below combining to the description of embodiment, wherein:
Fig. 1 is for being in schematic diagram when uninterruptedly providing low-temperature receiver, thermal source or domestic hot-water's output mode simultaneously according to the net for air-source heat pump units of the embodiment of the present invention;
Fig. 2 is for being in schematic diagram when meeting low-temperature receiver demand but also need the non-stop run shaping modes continuing to provide thermal source according to the net for air-source heat pump units of the embodiment of the present invention;
Fig. 3 is for being in schematic diagram when meeting thermal source demand but also need the non-stop run shaping modes continuing to provide low-temperature receiver according to the net for air-source heat pump units of the embodiment of the present invention;
Fig. 4 for be according to the net for air-source heat pump units of the embodiment of the present invention single thermal source is provided and the 4th finned heat exchanger is defrosted time schematic diagram;
Fig. 5 for be according to the net for air-source heat pump units of the embodiment of the present invention single thermal source is provided and the 3rd finned heat exchanger is defrosted time schematic diagram;
Fig. 6 for be according to the net for air-source heat pump units of the embodiment of the present invention single thermal source is provided and the second finned heat exchanger is defrosted time schematic diagram;
Fig. 7 for be according to the net for air-source heat pump units of the embodiment of the present invention single thermal source is provided and the first finned heat exchanger is defrosted time schematic diagram.
Reference numeral:
Net for air-source heat pump units 1000, compressor 10, exhaust outlet a, air entry b,
Four-way change-over valve 20, first valve port c, the second valve port d, the 3rd valve port e,
4th valve port f, the first finned heat exchanger 30a, the second finned heat exchanger 30b,
3rd finned heat exchanger 30c, the 4th finned heat exchanger 30d, the first cross valve 40a,
Second cross valve 40b, the 3rd cross valve 40c, the 4th cross valve 40d, the 5th valve port g,
6th valve port h, the 7th valve port i, the 8th valve port j, first throttle element 50,
First check valve 60a, the second check valve 60b, the 3rd check valve 60c,
4th check valve 60d, first heat restricting element 70a,
Second heat restricting element 70b, the 3rd heat restricting element 70c,
4th heat restricting element 70d, common line 80, shell and tube exchanger 90,
First row mouth of a river m, check-valves 100, control valve 110, falling-film heat exchanger 120,
First mouth of pipe k, the second mouth of pipe l, second row mouth of a river n, refrigeration restricting element 130,
Refrigeration check valve 140, first passage 150, second channel 160
Detailed description of the invention
Be described below in detail embodiments of the invention, the example of described embodiment is shown in the drawings, and wherein same or similar label represents same or similar element or has element that is identical or similar functions from start to finish.Being exemplary below by the embodiment be described with reference to the drawings, only for explaining the present invention, and can not limitation of the present invention being interpreted as.
In describing the invention, it will be appreciated that, orientation or the position relationship of the instruction such as term " " center ", " on ", D score, "front", "rear", "left", "right", " vertically ", " level ", " top ", " end ", " interior ", " outward " they be based on orientation shown in the drawings or position relationship; be only the present invention for convenience of description and simplified characterization; instead of instruction or imply the device of indication or element must have specific orientation, with specific azimuth configuration and operation, therefore can not be interpreted as limitation of the present invention.In addition, term " first ", " second " only for describing object, and can not be interpreted as instruction or hint relative importance or imply the quantity indicating indicated technical characteristic.Thus, be limited with " first ", the feature of " second " can express or impliedly comprise one or more these features.In describing the invention, except as otherwise noted, the implication of " multiple " is two or more.
In describing the invention, it should be noted that, unless otherwise clearly defined and limited, term " installation ", " being connected ", " connection " should be interpreted broadly, and such as, can be fixedly connected with, also can be removably connect, or connect integratedly; Can be mechanical connection, also can be electrical connection; Can be directly be connected, also indirectly can be connected by intermediary, can be the connection of two element internals.For the ordinary skill in the art, concrete condition above-mentioned term concrete meaning in the present invention can be understood.
Below with reference to Fig. 1-Fig. 7, the net for air-source heat pump units 1000 according to the embodiment of the present invention is described.It should be noted that, in following net for air-source heat pump units 1000, only describe the situation that this net for air-source heat pump units 1000 comprises four finned heat exchangers and four cross valves, but it should be noted that, the present invention is not limited thereto, what the technical staff of common art obviously knew is, reading the present invention's instruction disclosed herein, this embodiment can be applied to net for air-source heat pump units 1000 and comprise two, the finned heat exchanger of more than three and four and two, the situation of the cross valve of more than three and four, wherein, the quantity of finned heat exchanger and respectively one_to_one corresponding equal with the quantity of cross valve, this also drops within protection scope of the present invention, below net for air-source heat pump units 1000 is described in detail.
As shown in Fig. 1-Fig. 7, net for air-source heat pump units 1000 according to the embodiment of the present invention comprises: compressor 10, four-way change-over valve 20, four finned heat exchangers (30a, 30b, 30c, 30d), four cross valves (40a, 40b, 40c, 40d), shell and tube exchanger 90, falling-film heat exchanger 120, refrigeration restricting element 130 and refrigeration check valves 140, wherein, compressor 10 has exhaust outlet a and air entry b, it should be noted that, the structure of compressor 10 and operation principle etc. are prior art, are just not described in detail here.Particularly, compressor 10 is closed or semi-hermetic refrigerating compressor unit.More specifically, compressor 10 is helical-lobe compressor.
Four-way change-over valve 20 has the first valve port c, the second valve port d, the 3rd valve port e and the 4th valve port f, first valve port c is connected with exhaust outlet a, second valve port d is connected with air entry b, one of them conducting wherein in the first valve port c and the 3rd valve port e and the 4th valve port f, another conducting in the second valve port d and the 3rd valve port e and the 4th valve port f.
Four finned heat exchangers and four cross valve one_to_one corresponding, each cross valve comprises the 5th valve port g, the 6th valve port h, the 7th valve port i and the 8th valve port j, 5th valve port g of each cross valve is connected with exhaust outlet a, 6th valve port h of each cross valve is connected with one end of corresponding finned heat exchanger, 7th valve port i of each cross valve is connected with the 3rd valve port e, and the 8th valve port j of each cross valve is connected with the 3rd valve port e by first throttle element 50.Alternatively, first throttle element 50 is capillary.
Particularly, four cross valves are respectively the first cross valve 40a, the second cross valve 40b, the 3rd cross valve 40c and the 4th cross valve 40d.Four finned heat exchangers are respectively the first finned heat exchanger 30a, the second finned heat exchanger 30b, the 3rd finned heat exchanger 30c and the 4th finned heat exchanger 30d, the 5th valve port g of the first cross valve 40a is connected with exhaust outlet a, the 6th valve port h of the first cross valve 40a is connected with one end of the first finned heat exchanger 30a, the 7th valve port i of the first cross valve 40a is connected with the 3rd valve port e, and the 8th valve port j of the first cross valve 40a is connected with the 3rd valve port e by first throttle element 50.
The 5th valve port g of the second cross valve 40b is connected with exhaust outlet a, the 6th valve port h of the second cross valve 40b is connected with one end of the second finned heat exchanger 30b, the 7th valve port i of the second cross valve 40b is connected with the 3rd valve port e, and the 8th valve port j of the second cross valve 40b is connected with the 3rd valve port e by first throttle element 50.
The 5th valve port g of the 3rd cross valve 40c is connected with exhaust outlet a, the 6th valve port h of the 3rd cross valve 40c is connected with one end of the 3rd finned heat exchanger 30c, the 7th valve port i of the 3rd cross valve 40c is connected with the 3rd valve port e, and the 8th valve port j of the 3rd cross valve 40c is connected with the 3rd valve port e by first throttle element 50.
The 5th valve port g of the 4th cross valve 40d is connected with exhaust outlet a, the 6th valve port h of the 4th cross valve 40d is connected with one end of the 4th finned heat exchanger 30d, the 7th valve port i of the 4th cross valve 40d is connected with the 3rd valve port e, and the 8th valve port j of the 4th cross valve 40d is connected with the 3rd valve port e by first throttle element 50.
The other end of each finned heat exchanger is provided with a check valve and heats restricting element, and the outlet of each check valve is connected by common line 80 with each restricting element that heats.Alternatively, each restricting element that heats is electric expansion valve or heating power expansion valve.
Particularly, the other end of the first finned heat exchanger 30a is provided with a first check valve 60a and first and heats restricting element 70a, the outlet and first of the first check valve 60a is heated restricting element 70a and is connected by common line 80, specifically, the entrance of the first check valve 60a is connected with the first finned heat exchanger 30a, the outlet of the first check valve 60a is connected with common line 80, first two ends heating restricting element 70a are connected with common line 80 with the first finned heat exchanger 30a respectively, that is, it is in parallel that first check valve 60a and first heats restricting element 70a, and the first check valve 60a is from the first finned heat exchanger 30a to one-way conduction on the direction of common line 80.
The other end of the second finned heat exchanger 30b is provided with a second check valve 60b and second and heats restricting element 70b, the outlet and second of the second check valve 60b is heated restricting element 70b and is connected by common line 80, specifically, the entrance of the second check valve 60b is connected with the second finned heat exchanger 30b, the outlet of the second check valve 60b is connected with common line 80, second two ends heating restricting element 70b are connected with common line 80 with the second finned heat exchanger 30b respectively, that is, it is in parallel that second check valve 60b and second heats restricting element 70b, and the second check valve 60b is from the second finned heat exchanger 30b to one-way conduction on the direction of common line 80.
The other end of the 3rd finned heat exchanger 30c is provided with a 3rd check valve 60c and the 3rd and heats restricting element 70c, the outlet and the 3rd of the 3rd check valve 60c is heated restricting element 70c and is connected by common line 80, specifically, the entrance of the 3rd check valve 60c is connected with the 3rd finned heat exchanger 30c, the outlet of the 3rd check valve 60c is connected with common line 80, 3rd two ends heating restricting element 70c are connected with common line 80 with the 3rd finned heat exchanger 30c respectively, that is, it is in parallel that 3rd check valve 60c and the 3rd heats restricting element 70c, and the 3rd check valve 60c is from the 3rd finned heat exchanger 30c to one-way conduction on the direction of common line 80.
The other end of the 4th finned heat exchanger 30d is provided with a 4th check valve 60d and the 4th and heats restricting element 70d, the outlet and the 4th of the 4th check valve 60d is heated restricting element 70d and is connected by common line 80, specifically, the entrance of the 4th check valve 60d is connected with the 4th finned heat exchanger 30d, the outlet of the 4th check valve 60d is connected with common line 80, 4th two ends heating restricting element 70d are connected with common line 80 with the 4th finned heat exchanger 30d respectively, that is, it is in parallel that 4th check valve 60d and the 4th heats restricting element 70d, and the 4th check valve 60d is from the 4th finned heat exchanger 30d to one-way conduction on the direction of common line 80.
One end of shell and tube exchanger 90 is connected with the 4th valve port f, the other end of shell and tube exchanger 90 is connected with common line 80 with control valve 110 by check-valves 100, particularly, control valve 110 has open mode and closed condition, the import of check-valves 100 is connected with the other end of shell and tube exchanger 90, the outlet of check-valves 100 is connected with one end of control valve 110, the other end of control valve 110 is connected with common line 80, that is, check-valves 100 one-way conduction on the direction from the other end of shell and tube exchanger 90 to control valve 110.Wherein, shell and tube exchanger 90 is provided with first row mouth of a river m, and the structure of shell and tube exchanger 90 and operation principle etc. are prior art, are just not described in detail here.Alternatively, control valve 110 is magnetic valve.
Falling-film heat exchanger 120 has the first mouth of pipe k and the second mouth of pipe l, and the first mouth of pipe k is connected with air entry b, and the second mouth of pipe l is connected with the other end of shell and tube exchanger 90.Refrigeration restricting element 130 is connected with the second mouth of pipe l.Particularly, the restricting element 130 that freezes has open mode and closed condition.Alternatively, the restricting element 130 that freezes is electric expansion valve.Refrigeration check valve 140 import be connected with common line 80 and the outlet of the check valve 140 that freeze with refrigeration restricting element 130 be connected, that is, freeze check valve 140 from common line 80 to freeze restricting element 130 direction on one-way conduction.Wherein, falling-film heat exchanger 120 also has second row mouth of a river n, it should be noted that, the structure of falling-film heat exchanger 120 and operation principle etc. are prior art, are just not described in detail here.
As shown in Figure 1, uninterruptedly provide low-temperature receiver when net for air-source heat pump units 1000 is in simultaneously, when thermal source or domestic hot-water's output mode, first valve port c of four-way change-over valve 20 and the 4th valve port f conducting and the second valve port d and the 3rd valve port e conducting, first cross valve 40a, second cross valve 40b, 3rd cross valve 40c and the 4th cross valve 40d is in the 5th valve port g and the 8th valve port j conducting and the state of the 6th valve port h and the 7th valve port i conducting respectively, control valve 110 is in closed condition, refrigeration restricting element 130 is in open mode, because the fluid resistance between the 4th valve port f and shell and tube exchanger 90 is less than the fluid resistance between the 5th valve port g and the 8th valve port j, now as illustrated by the arrows in fig. 1, the gas coolant of the HTHP of discharging from the exhaust outlet a of compressor 10 enters in shell and tube exchanger 90 by four-way change-over valve 20, refrigerant becomes liquid after release heat in shell and tube exchanger 90, liquid coolant flows through check-valves 100 and enters in refrigeration restricting element 130, refrigerant enters in falling-film heat exchanger 120 after reducing pressure by regulating flow in refrigeration restricting element 130, refrigerant becomes gas after absorbing heat in falling-film heat exchanger 120 and evaporating, gas coolant is sucked by compressor 10 by the connecting line between falling-film heat exchanger 120 and compressor 10 and air entry b, refrigerant is discharged after second compression in compressor 10 again, form kind of refrigeration cycle.
Due to refrigerant release heat in shell and tube exchanger 90, thus thermal source or domestic hot-water can be provided at the m place, the first row mouth of a river of shell and tube exchanger 90 to use side, when using side to be set as domestic hot-water's demand, net for air-source heat pump units 1000 can improve the temperature value at the m place, the first row mouth of a river of shell and tube exchanger 90 automatically.
Because refrigerant absorbs heat evaporation in falling-film heat exchanger 120, thus low-temperature receiver can be provided at the n place, the second row mouth of a river of falling-film heat exchanger 120 to use side.Net for air-source heat pump units 1000 can provide thermal source and low-temperature receiver simultaneously thus, and thermal source and refrigerant can be utilized simultaneously, without the need to release heat in finned heat exchanger or absorb heat, the using energy source of net for air-source heat pump units 1000 reaches maximum.
As shown in Figure 2, when net for air-source heat pump units 1000 be in meet low-temperature receiver demand but also need the non-stop run shaping modes continuing to provide thermal source time, first valve port c of four-way change-over valve 20 and the 4th valve port f conducting and the second valve port d and the 3rd valve port e conducting, first cross valve 40a, the second cross valve 40b, the 3rd cross valve 40c and the 4th cross valve 40d are in the 5th valve port g and the 8th valve port j conducting and the state of the 6th valve port h and the 7th valve port i conducting respectively, refrigeration restricting element 130 is in closed condition, and control valve 110 is in open mode.Now as denoted by the arrows in fig. 2, the gas coolant of the HTHP of discharging from the exhaust outlet a of compressor 10 enters into shell and tube exchanger 90 through four-way change-over valve 20, gas coolant is turned into liquid after release heat in shell and tube exchanger 90, liquid coolant flows through check-valves 100 and control valve 110 enters in common line 80, refrigerant in common line 80 heats restricting element 70a respectively through first, second heats restricting element 70b, 3rd heats after restricting element 70c and the 4th heats the reducing pressure by regulating flow of restricting element 70d and enters into the first finned heat exchanger 30a, second finned heat exchanger 30b, in 3rd finned heat exchanger 30c and the 4th finned heat exchanger 30d, refrigerant absorbs heat evaporation to become gas in four finned heat exchangers, the gas coolant of discharging from each finned heat exchanger enters in four-way change-over valve 20 through corresponding cross valve, rear discharge is re-compressed after the refrigerant of four-way change-over valve 20 outflow is sucked by compressor 10, form heat pump cycle.Now due to refrigerant release heat in shell and tube exchanger 90, thermal source or domestic hot-water can be provided at the m place, the first row mouth of a river of shell and tube exchanger 90 to use side thus.
As shown in Figure 3, when net for air-source heat pump units 1000 be in meet thermal source demand but also need the non-stop run shaping modes continuing to provide low-temperature receiver time, first valve port c of four-way change-over valve 20 and the 3rd valve port e conducting and the second valve port d and the 4th valve port f conducting, first cross valve 40a, the second cross valve 40b, the 3rd cross valve 40c and the 4th cross valve 40d are in the 5th valve port g and the 8th valve port j conducting and the state of the 6th valve port h and the 7th valve port i conducting respectively, control valve 110 is in closed condition, and refrigeration restricting element 130 is in open mode.Now as indicated by the arrows in fig. 3, the seven valve port i of gas coolant respectively from four cross valves after four-way change-over valve 20 of the HTHP of discharging from the exhaust outlet a of compressor 10 enters in four cross valves, the refrigerant entered in each cross valve enters in corresponding finned heat exchanger through the 6th valve port h, be turned into liquid after entering into the refrigerant release heat in four finned heat exchangers, the refrigerant liquid in each finned heat exchanger is drained in common line 80 through corresponding check valve.Refrigerant in common line 80 enters into refrigeration restricting element 130 through refrigeration check valve 140 and carries out reducing pressure by regulating flow, refrigerant after reducing pressure by regulating flow enters in falling-film heat exchanger 120, refrigerant absorbs heat after evaporation is turned into gas and discharges in falling-film heat exchanger 120, discharge after the refrigerant of falling-film heat exchanger 120 discharge again compresses after the connecting line between falling-film heat exchanger 120 and compressor 10 is sucked by compressor 10, form kind of refrigeration cycle.Because refrigerant absorbs heat evaporation in falling-film heat exchanger 120, thus low-temperature receiver can be provided at the n place, the second row mouth of a river of falling-film heat exchanger 120 to use side.
As shown in Figure 4, when net for air-source heat pump units 1000 be in single thermal source is provided and the 4th finned heat exchanger 30d is defrosted time, first valve port c of four-way change-over valve 20 and the 4th valve port f conducting and the second valve port d and the 3rd valve port e conducting, 4th cross valve 40d carries out commutating the 5th valve port g and the 6th valve port h conducting and the 7th valve port i and the 8th valve port j conducting that make the 4th cross valve 40d, first cross valve 40a, second cross valve 40b, 3rd cross valve 40c remains unchanged maintenance the 5th valve port g and the 8th valve port j conducting and the state of the 6th valve port h and the 7th valve port i conducting, refrigeration restricting element 130 is in closed condition, control valve 110 is in open mode.Now as shown by the arrows in figure 4, the high temperature and high pressure gas refrigerant of discharging from the exhaust outlet a of compressor 10 is divided into two-way to circulate, wherein a road enters into shell and tube exchanger 90 through four-way change-over valve 20, and this road refrigerant is turned into liquid state after release heat and flows through check-valves 100 and control valve 110 enters into common line 80 in shell and tube exchanger 90.
Another road refrigerant enters in the 4th cross valve 40d by the 5th valve port g of the 4th cross valve 40d simultaneously, this road refrigerant is drained into the 4th finned heat exchanger 30d from the 6th valve port h of the 4th cross valve 40d, refrigerant is turned into liquid after release heat in the 4th finned heat exchanger 30d, the frost layer on the 4th finned heat exchanger 30d surface is melted by the heat utilizing refrigerant to discharge, and the liquid coolant in the 4th finned heat exchanger 30d enters into common line 80 through the 4th check valve 60d and converges with the refrigerant flowing through control valve 110.Refrigerant after converging flows through first respectively and heats restricting element 70a, second and heat after restricting element 70b and the 3rd heats restricting element 70c reducing pressure by regulating flow and enter in the first finned heat exchanger 30a, the second finned heat exchanger 30b and the 3rd finned heat exchanger 30c, refrigerant evaporation of absorbing heat in the first finned heat exchanger 30a, the second finned heat exchanger 30b and the 3rd finned heat exchanger 30c becomes gas, and gas coolant is sucked by compressor 10 respectively by the first cross valve 40a, the second cross valve 40b and the 3rd cross valve 40c enter in four-way change-over valve 20 again.Be re-compressed rear discharge by the refrigerant that compressor 10 sucks, form heat pump cycle.Now due to cold-producing medium release heat in shell and tube exchanger 90, therefore thermal source or domestic hot-water can be provided at the first row mouth of a river m of shell and tube exchanger 90 to use side.
As shown in Figure 5, when net for air-source heat pump units 1000 be in single thermal source is provided and the 3rd finned heat exchanger 30c is defrosted time, first valve port c of four-way change-over valve 20 and the 4th valve port f conducting and the second valve port d and the 3rd valve port e conducting, 3rd cross valve 40c carries out commutating the 5th valve port g and the 6th valve port h conducting and the 7th valve port i and the 8th valve port j conducting that make the 3rd cross valve 40c, first cross valve 40a, second cross valve 40b, 4th cross valve 40d remains unchanged maintenance the 5th valve port g and the 8th valve port j conducting and the state of the 6th valve port h and the 7th valve port i conducting, refrigeration restricting element 130 is in closed condition, control valve 110 is in open mode.Now as illustrated by arrows 5, the high temperature and high pressure gas refrigerant of discharging from the exhaust outlet a of compressor 10 is divided into two-way to circulate, wherein a road enters into shell and tube exchanger 90 through four-way change-over valve 20, and this road refrigerant is turned into liquid state after release heat and flows through check-valves 100 and control valve 110 enters into common line 80 in shell and tube exchanger 90.
Another road refrigerant enters in the 3rd cross valve 40c by the 5th valve port g of the 3rd cross valve 40c simultaneously, this road refrigerant is drained into the 3rd finned heat exchanger 30c from the 6th valve port h of the 3rd cross valve 40c, refrigerant is turned into liquid after release heat in the 3rd finned heat exchanger 30c, the frost layer on the 3rd finned heat exchanger 30c surface is melted by the heat utilizing refrigerant to discharge, and the liquid coolant in the 3rd finned heat exchanger 30c enters into common line 80 through the 3rd check valve 60c and converges with the refrigerant flowing through control valve 110.Refrigerant after converging flows through first respectively and heats restricting element 70a, second and heat after restricting element 70b and the 4th heats restricting element 70d reducing pressure by regulating flow and enter in the first finned heat exchanger 30a, the second finned heat exchanger 30b and the 4th finned heat exchanger 30d, refrigerant evaporation of absorbing heat in the first finned heat exchanger 30a, the second finned heat exchanger 30b and the 4th finned heat exchanger 30d becomes gas, and gas coolant is sucked by compressor 10 respectively by the first cross valve 40a, the second cross valve 40b and the 4th cross valve 40d enter in four-way change-over valve 20 again.Be re-compressed rear discharge by the refrigerant that compressor 10 sucks, form heat pump cycle.Now due to cold-producing medium release heat in shell and tube exchanger 90, therefore thermal source or domestic hot-water can be provided at the first row mouth of a river m of shell and tube exchanger 90 to use side.
As shown in Figure 6, when net for air-source heat pump units 1000 be in single thermal source is provided and the second finned heat exchanger 30b is defrosted time, first valve port c of four-way change-over valve 20 and the 4th valve port f conducting and the second valve port d and the 3rd valve port e conducting, second cross valve 40b carries out commutating the 5th valve port g and the 6th valve port h conducting and the 7th valve port i and the 8th valve port j conducting that make the second cross valve 40b, first cross valve 40a, 3rd cross valve 40c, 4th cross valve 40d remains unchanged maintenance the 5th valve port g and the 8th valve port j conducting and the state of the 6th valve port h and the 7th valve port i conducting, refrigeration restricting element 130 is in closed condition, control valve 110 is in open mode.Now as indicated by the arrows in fig. 6, the high temperature and high pressure gas refrigerant of discharging from the exhaust outlet a of compressor 10 is divided into two-way to circulate, wherein a road enters into shell and tube exchanger 90 through four-way change-over valve 20, and this road refrigerant is turned into liquid state after release heat and flows through check-valves 100 and control valve 110 enters into common line 80 in shell and tube exchanger 90.
Another road refrigerant enters in the second cross valve 40b by the 5th valve port g of the second cross valve 40b simultaneously, this road refrigerant is drained into the second finned heat exchanger 30b from the 6th valve port h of the second cross valve 40b, refrigerant is turned into liquid after release heat in the second finned heat exchanger 30b, the frost layer on the second finned heat exchanger 30b surface is melted by the heat utilizing refrigerant to discharge, and the liquid coolant in the second finned heat exchanger 30b enters into common line 80 through the second check valve 60b and converges with the refrigerant flowing through control valve 110.Refrigerant after converging flows through first respectively and heats restricting element 70a, the 3rd and heat after restricting element 70c and the 4th heats restricting element 70d reducing pressure by regulating flow and enter in the first finned heat exchanger 30a, the 3rd finned heat exchanger 30c and the 4th finned heat exchanger 30d, refrigerant evaporation of absorbing heat in the first finned heat exchanger 30a, the 3rd finned heat exchanger 30c and the 4th finned heat exchanger 30d becomes gas, and gas coolant is sucked by compressor 10 respectively by the first cross valve 40a, the 3rd cross valve 40c and the 4th cross valve 40d enter in four-way change-over valve 20 again.Be re-compressed rear discharge by the refrigerant that compressor 10 sucks, form heat pump cycle.Now due to cold-producing medium release heat in shell and tube exchanger 90, therefore thermal source or domestic hot-water can be provided at the first row mouth of a river m of shell and tube exchanger 90 to use side.
As shown in Figure 7, when net for air-source heat pump units 1000 be in single thermal source is provided and the first finned heat exchanger 30a is defrosted time, first valve port c of four-way change-over valve 20 and the 4th valve port f conducting and the second valve port d and the 3rd valve port e conducting, first cross valve 40a carries out commutating the 5th valve port g and the 6th valve port h conducting and the 7th valve port i and the 8th valve port j conducting that make the first cross valve 40a, second cross valve 40b, 3rd cross valve 40c, 4th cross valve 40d remains unchanged maintenance the 5th valve port g and the 8th valve port j conducting and the state of the 6th valve port h and the 7th valve port i conducting, refrigeration restricting element 130 is in closed condition, control valve 110 is in open mode.Now as depicted by the arrows in figure 7, the high temperature and high pressure gas refrigerant of discharging from the exhaust outlet a of compressor 10 is divided into two-way to circulate, wherein a road enters into shell and tube exchanger 90 through four-way change-over valve 20, and this road refrigerant is turned into liquid state after release heat and flows through check-valves 100 and control valve 110 enters into common line 80 in shell and tube exchanger 90.
Another road refrigerant enters in the first cross valve 40a by the 5th valve port g of the first cross valve 40a simultaneously, this road refrigerant is drained into the first finned heat exchanger 30a from the 6th valve port h of the first cross valve 40a, refrigerant is turned into liquid after release heat in the first finned heat exchanger 30a, the frost layer on the first finned heat exchanger 30a surface is melted by the heat utilizing refrigerant to discharge, and the liquid coolant in the first finned heat exchanger 30a enters into common line 80 through the first check valve 60a and converges with the refrigerant flowing through control valve 110.Refrigerant after converging flows through second respectively and heats restricting element 70b, the 3rd and heat after restricting element 70c and the 4th heats restricting element 70d reducing pressure by regulating flow and enter in the second finned heat exchanger 30b, the 3rd finned heat exchanger 30c and the 4th finned heat exchanger 30d, refrigerant evaporation of absorbing heat in the second finned heat exchanger 30b, the 3rd finned heat exchanger 30c and the 4th finned heat exchanger 30d becomes gas, and gas coolant is sucked by compressor 10 respectively by the second cross valve 40b, the 3rd cross valve 40c and the 4th cross valve 40d enter in four-way change-over valve 20 again.Be re-compressed rear discharge by the refrigerant that compressor 10 sucks, form heat pump cycle.Now due to cold-producing medium release heat in shell and tube exchanger 90, therefore thermal source or domestic hot-water can be provided at the first row mouth of a river m of shell and tube exchanger 90 to use side.
Wherein, it should be noted that, four cross valves work independently, namely non-interference between four cross valves, above-mentioned description is illustrating of the refrigerant circulation of net for air-source heat pump units 1000 when need defrost to a finned heat exchanger, and what be worth understanding is, the present invention is not limited thereto, when net for air-source heat pump units 1000 is in heating operation, can defrost to two or three finned heat exchangers simultaneously, also can carry out circulating defrosting in turn to four finned heat exchangers.The finned heat exchanger wherein carrying out defrosting can be combined the defrost process of carrying out sequencing.
According to the net for air-source heat pump units 1000 of the embodiment of the present invention, by being provided with multiple finned heat exchanger, multiple cross valve, shell and tube exchanger 90 and falling-film heat exchanger 120, thus low-temperature receiver and thermal source or domestic hot-water not only can be uninterruptedly provided to use side simultaneously, low-temperature receiver and thermal source are all utilized, improve the efficiency of net for air-source heat pump units 1000, also can carry out the utilization of single low-temperature receiver or thermal source simultaneously, and can by providing the pattern seamless switching of low-temperature receiver and thermal source for providing the pattern of single low-temperature receiver or thermal source simultaneously.And uninterruptedly provide thermal source when can defrost to finned heat exchanger in the winter time according to the net for air-source heat pump units 1000 of the embodiment of the present invention, avoid traditional Temperature cycling sharply decline in use side of causing because finned heat exchanger defrosting and the comfortableness brought reduces, improve the comfort of user, and heating operation is continual and steady during defrosting, system pressure is not caused to change, therefore compressor 10 is not impacted, extend the service life of compressor 10.
As shown in Fig. 1-Fig. 7, in specific embodiments more of the present invention, the 5th valve port g of multiple cross valve is communicated with by first passage 150, and first passage 150 is connected with exhaust outlet a.That is, the 5th valve port g, the 5th valve port g of the second cross valve 40b of the first cross valve 40a, the 5th valve port g of the 3rd cross valve 40c are communicated with by first passage 150 with the 5th valve port g of the 4th cross valve 40d.Thus make the structure of net for air-source heat pump units 1000 simple.
According to some embodiments of the present invention, as shown in Fig. 1-Fig. 7,7th valve port i of multiple cross valve is communicated with by second channel 160, and the 3rd valve port e is connected with second channel 160, and the 8th valve port j of each cross valve is connected to second channel 160 by first throttle element 50.That is, the 7th valve port i, the 7th valve port i of the second cross valve 40b of the first cross valve 40a, the 7th valve port i of the 3rd cross valve 40c are communicated with by second channel 160 with the 7th valve port i of the 4th cross valve 40d.The 8th valve port j of the first cross valve 40a is connected to second channel 160 by first throttle element 50, the 8th valve port j of the second cross valve 40b is connected to second channel 160 by first throttle element 50, the 8th valve port j of the 3rd cross valve 40c is connected to second channel 160 by first throttle element 50, and the 8th valve port j of the 4th cross valve 40d is connected to second channel 160 by first throttle element 50.Thus make the structure of net for air-source heat pump units 1000 simple.
In the description of this description, specific features, structure, material or feature that the description of reference term " embodiment ", " some embodiments ", " illustrative examples ", " example ", " concrete example " or " some examples " etc. means to describe in conjunction with this embodiment or example are contained at least one embodiment of the present invention or example.In this manual, identical embodiment or example are not necessarily referred to the schematic representation of above-mentioned term.And the specific features of description, structure, material or feature can combine in an appropriate manner in any one or more embodiment or example.
Although illustrate and describe embodiments of the invention, those having ordinary skill in the art will appreciate that: can carry out multiple change, amendment, replacement and modification to these embodiments when not departing from principle of the present invention and aim, scope of the present invention is by claim and equivalents thereof.
Claims (9)
1. a net for air-source heat pump units, is characterized in that, comprising:
Compressor, described compressor has exhaust outlet and air entry;
Four-way change-over valve, described four-way change-over valve has first to fourth valve port, and described first valve port is connected with described exhaust outlet, and described second valve port is connected with described air entry;
Multiple finned heat exchanger and multiple cross valve, described multiple finned heat exchanger and described multiple cross valve one_to_one corresponding, each described cross valve comprises the 5th to the 8th valve port, described 5th valve port of each described cross valve is connected with described exhaust outlet, described 6th valve port of each described cross valve is connected with one end of corresponding described finned heat exchanger, described 7th valve port of each described cross valve is connected with described 3rd valve port, described 8th valve port of each described cross valve is connected with described 3rd valve port by first throttle element, the other end of each described finned heat exchanger is provided with a check valve and heats restricting element, the outlet of each described check valve with each described in heat restricting element and be connected by common line,
Shell and tube exchanger, one end of described shell and tube exchanger is connected with described 4th valve port, and the other end of described shell and tube exchanger is connected with described common line with control valve by check-valves;
Falling-film heat exchanger, described falling-film heat exchanger has first mouth of pipe and second mouth of pipe, and described first mouth of pipe is connected with described air entry, and described second mouth of pipe is connected with the other end of described shell and tube exchanger;
Refrigeration restricting element, described refrigeration restricting element is connected with described second mouth of pipe;
Refrigeration check valve, the import of described refrigeration check valve is connected with described common line and exports and is connected with described refrigeration restricting element.
2. net for air-source heat pump units according to claim 1, is characterized in that, described 5th valve port of described multiple cross valve is communicated with by first passage, and described first passage is connected with described exhaust outlet.
3. net for air-source heat pump units according to claim 1, is characterized in that, described 7th valve port of described multiple cross valve is communicated with by second channel, and described 3rd valve port is connected with described second channel.
4. net for air-source heat pump units according to claim 3, is characterized in that, described 8th valve port of each described cross valve is connected to described second channel by first throttle element.
5. net for air-source heat pump units according to claim 1, is characterized in that, described control valve is magnetic valve.
6. net for air-source heat pump units according to claim 1, is characterized in that, described refrigeration restricting element is electric expansion valve.
7. net for air-source heat pump units according to claim 1, is characterized in that, heating restricting element described in each is electric expansion valve or heating power expansion valve.
8. net for air-source heat pump units according to claim 1, is characterized in that, described compressor is closed or semi-hermetic refrigerating compressor unit.
9. net for air-source heat pump units according to claim 8, is characterized in that, described compressor is helical-lobe compressor.
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| CN106642793A (en) * | 2017-03-08 | 2017-05-10 | 王维洲 | Multifunctional air source heat pump unit capable of uninterrupted heating |
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