CN203785316U - Air source heat pump unit - Google Patents
Air source heat pump unit Download PDFInfo
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- CN203785316U CN203785316U CN201320816554.XU CN201320816554U CN203785316U CN 203785316 U CN203785316 U CN 203785316U CN 201320816554 U CN201320816554 U CN 201320816554U CN 203785316 U CN203785316 U CN 203785316U
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Abstract
The utility model discloses an air source heat pump unit which comprises a compressor, four-way reversing valves, a plurality of fin type heat exchangers, a plurality of four-way valves, a shell and tube heat exchanger, a falling film type heat exchanger, a refrigeration throttling element and a refrigeration one-way valve. Each four-way reversing valve comprises a fifth valve port, a sixth valve port, a seventh valve port and an eighth valve port, the fifth valve ports are connected with an air outlet, the sixth valve ports are connected with the fin type 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 fin type heat exchanger is provided with a one-way valve and a heating throttling element, and an outlet of each one-way valve is connected with the corresponding heating throttling element through a public pipe. The shell and tube heat exchanger is connected with the public pipe through a check valve and a control valve. The falling film type heat exchanger is connected with an air sucking opening and the shell and tube heat exchanger. According to the air source heat pump unit, a cold source and a heat source or domestic hot water are continuously provided for the using side at the same side, and the use comfort of a user is improved.
Description
Technical field
The utility model relates to refrigerating field, especially relates 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 in the time that low-temperature receiver and thermal source demand are provided, all needs unwanted cold or heat to be discharged in atmosphere, 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 commutate to transfer to refrigeration mode in defrost process, the refrigerant changing in finned heat exchanger flows to carry out reverse cycle defrosting.In reverse cycle defrosting process, because refrigerant pressure oscillation is larger to compressor impact, can shorten the service life of compressor, in reverse cycle defrosting process, use side heat source temperature periodically sharply to decline and cause comfortableness to reduce simultaneously.
Utility model content
The utility model is intended at least solve one of technical problem existing in prior art.For this reason, an object of the present utility model is to propose a kind of net for air-source heat pump units, can be uninterruptedly simultaneously to using side that low-temperature receiver and thermal source or domestic hot-water are provided.
According to net for air-source heat pump units of the present utility model, 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 the first valve port is connected with described exhaust outlet, and described the second valve port is connected with described air entry, multiple finned heat exchangers and multiple cross valve, described multiple finned heat exchanger and described multiple cross valve are corresponding one by one, each described cross valve comprises the 5th to the 8th valve port, described the 5th valve port of each described cross valve is connected with described exhaust outlet, described the 6th valve port of each described cross valve is connected with one end of corresponding described finned heat exchanger, described the 7th valve port of each described cross valve is connected with described the 3rd valve port, described the 8th valve port of each described cross valve is connected with described the 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 the 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 type heat exchanger, described falling film type 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 outlet is connected with described refrigeration restricting element.
According to net for air-source heat pump units of the present utility model, by being provided with multiple finned heat exchangers, multiple cross valve, shell and tube exchanger and falling film type heat exchanger, thereby not only can be uninterruptedly simultaneously to using side that low-temperature receiver and thermal source or domestic hot-water are provided, 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 be by provide the pattern seamless switching of low-temperature receiver and thermal source for the pattern of single low-temperature receiver or thermal source is provided simultaneously.And can defrost to finned heat exchanger in the winter time according to net for air-source heat pump units of the present utility model time, uninterruptedly provide thermal source, avoiding traditional reduces because of the finned heat exchanger impatient acute comfortableness of bringing that declines of use side temperature cycle causing that defrosts, improve user's comfort, and heating operation is continual and steady during defrosting, do not cause that system pressure changes, therefore compressor is not impacted, extended the service life of compressor.
In addition, also there is following additional technical feature according to net for air-source heat pump units of the present utility model:
In embodiment more of the present utility model, described the 5th valve port of described multiple cross valves is communicated with by first passage, and described first passage is connected with described exhaust outlet.Thereby make the simple in structure of net for air-source heat pump units.
According to embodiment more of the present utility model, described the 7th valve port of described multiple cross valves is communicated with by second channel, and described the 3rd valve port is connected with described second channel.Thereby make the simple in structure of net for air-source heat pump units.
Further, described the 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, described in each, heating restricting element 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 utility model and advantage in the following description part provide, and part will become obviously from the following description, or recognize by practice of the present utility model.
Brief description of the drawings
Above-mentioned and/or additional aspect of the present utility model and advantage accompanying drawing below combination is understood becoming the description of embodiment obviously and easily, wherein:
Fig. 1 is the schematic diagram in the time uninterruptedly simultaneously providing low-temperature receiver, thermal source or domestic hot-water's output mode according to the net for air-source heat pump units of the utility model embodiment;
Fig. 2 is the schematic diagram in meeting low-temperature receiver demand but while also needing to continue to provide the non-stop run of thermal source to regulate pattern according to the net for air-source heat pump units of the utility model embodiment;
Fig. 3 is the schematic diagram in meeting thermal source demand but while also needing to continue to provide the non-stop run of low-temperature receiver to regulate pattern according to the net for air-source heat pump units of the utility model embodiment;
Fig. 4 for according to the net for air-source heat pump units of the utility model embodiment in single schematic diagram when thermal source being provided and the 4th finned heat exchanger being defrosted;
Fig. 5 for according to the net for air-source heat pump units of the utility model embodiment in single schematic diagram when thermal source being provided and the 3rd finned heat exchanger being defrosted;
Fig. 6 for according to the net for air-source heat pump units of the utility model embodiment in single schematic diagram when thermal source being provided and the second finned heat exchanger being defrosted;
Fig. 7 for according to the net for air-source heat pump units of the utility model embodiment in single schematic diagram when thermal source being provided and the first finned heat exchanger being defrosted.
Reference numeral:
Net for air-source heat pump units 1000, compressor 10, exhaust outlet a, air entry b,
Four-way change-over valve 20, the first valve port c, the second valve port d, the 3rd valve port e,
The 4th valve port f, the first finned heat exchanger 30a, the second finned heat exchanger 30b,
The 3rd finned heat exchanger 30c, the 4th finned heat exchanger 30d, the first cross valve 40a,
The second cross valve 40b, the 3rd cross valve 40c, the 4th cross valve 40d, the 5th valve port g,
The 6th valve port h, the 7th valve port i, the 8th valve port j, first throttle element 50,
The first check valve 60a, the second check valve 60b, the 3rd check valve 60c,
The 4th check valve 60d, first heat restricting element 70a,
Second heat restricting element 70b, the 3rd heat restricting element 70c,
The 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 type heat exchanger 120,
The 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
Describe embodiment of the present utility model below in detail, the example of described embodiment is shown in the drawings, and wherein same or similar label represents same or similar element or has the element of identical or similar functions from start to finish.Be exemplary below by the embodiment being described with reference to the drawings, only for explaining the utility model, and can not be interpreted as restriction of the present utility model.
In description of the present utility model, it will be appreciated that, term " " center ", " on ", D score, " front ", " afterwards ", " left side ", " right side ", " vertically ", " level ", " top ", " end ", " interior ", orientation or the position relationship of instructions such as " outward " are based on orientation shown in the drawings or position relationship, only the utility model and simplified characterization for convenience of description, instead of device or the element of instruction or hint indication must have specific orientation, with specific orientation structure and operation, therefore can not be interpreted as restriction of the present utility model.In addition, term " first ", " second " be only for describing object, and can not be interpreted as instruction or hint relative importance or the implicit quantity that indicates indicated technical characterictic.Thus, one or more these features can be expressed or impliedly be comprised to the feature that is limited with " first ", " second ".In description of the present utility model, except as otherwise noted, the implication of " multiple " is two or more.
In description of the present utility model, it should be noted that, unless otherwise clearly defined and limited, term " installation ", " being connected ", " connection " should be interpreted broadly, and for example, can be to be fixedly connected with, and can be also to removably connect, or connect integratedly; Can be mechanical connection, can be also electrical connection; Can be to be directly connected, also can indirectly be connected by intermediary, can be the connection of two element internals.For the ordinary skill in the art, can concrete condition understand the concrete meaning of above-mentioned term in the utility model.
Describe according to the net for air-source heat pump units 1000 of the utility model embodiment below with reference to Fig. 1-Fig. 7.It should be noted that, in following net for air-source heat pump units 1000, the situation that this net for air-source heat pump units 1000 comprises four finned heat exchangers and four cross valves has only been described, but it should be noted that, the utility model is not limited to this, what the technical staff in ordinary skill field obviously knew is, reading the utility model instruction disclosed herein, this embodiment can be applied to net for air-source heat pump units 1000 and comprise two, the finned heat exchanger that three and four are above and two, the situation of three and four above cross valves, wherein, the quantity of finned heat exchanger and the quantity of cross valve equate and are corresponding one by one respectively, within this also drops into protection domain of the present utility model, below net for air-source heat pump units 1000 is elaborated.
As shown in Fig. 1-Fig. 7, comprise according to the net for air-source heat pump units 1000 of the utility model embodiment: 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 type 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, structure and the operation principle etc. of compressor 10 are prior art, are not just 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, the first valve port c is connected with exhaust outlet a, the second valve port d is connected with air entry b, wherein one of them conducting 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 valves are corresponding one by one, 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, the 5th valve port g of each cross valve is connected with exhaust outlet a, the 6th valve port h of each cross valve is connected with one end of corresponding finned heat exchanger, the 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 of the first check valve 60a and first heats restricting element 70a and is connected by common line 80, particularly, 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, the first two ends that heat restricting element 70a are connected with common line 80 with the first finned heat exchanger 30a respectively, that is to say, the first check valve 60a and first heats restricting element 70a parallel connection, and the first check valve 60a one-way conduction from the first finned heat exchanger 30a to 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 of the second check valve 60b and second heats restricting element 70b and is connected by common line 80, particularly, 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, the second two ends that heat restricting element 70b are connected with common line 80 with the second finned heat exchanger 30b respectively, that is to say, the second check valve 60b and second heats restricting element 70b parallel connection, and the second check valve 60b one-way conduction from the second finned heat exchanger 30b to 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 of the 3rd check valve 60c and the 3rd heats restricting element 70c and is connected by common line 80, particularly, 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, the 3rd two ends that heat restricting element 70c are connected with common line 80 with the 3rd finned heat exchanger 30c respectively, that is to say, the 3rd check valve 60c and the 3rd heats restricting element 70c parallel connection, and the 3rd check valve 60c one-way conduction from the 3rd finned heat exchanger 30c to 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 of the 4th check valve 60d and the 4th heats restricting element 70d and is connected by common line 80, particularly, 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, the 4th two ends that heat restricting element 70d are connected with common line 80 with the 4th finned heat exchanger 30d respectively, that is to say, the 4th check valve 60d and the 4th heats restricting element 70d parallel connection, and the 4th check valve 60d one-way conduction from the 4th finned heat exchanger 30d to 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 to say check-valves 100 one-way conduction from the other end of shell and tube exchanger 90 to the direction of control valve 110.Wherein, shell and tube exchanger 90 is provided with first row mouth of a river m, and structure and the operation principle etc. of shell and tube exchanger 90 are prior art, are not just described in detail here.Alternatively, control valve 110 is magnetic valve.
Falling film type 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, refrigeration restricting element 130 has open mode and closed condition.Alternatively, refrigeration restricting element 130 is electric expansion valve.The import of refrigeration check valve 140 is connected with common line 80 and the outlet of the check valve 140 that freezes is connected with refrigeration restricting element 130, that is to say, refrigeration check valve 140 is one-way conduction on the direction from common line 80 to refrigeration restricting element 130.Wherein, falling film type heat exchanger 120 also has second row mouth of a river n, it should be noted that, structure and the operation principle etc. of falling film type heat exchanger 120 are prior art, are not just described in detail here.
As shown in Figure 1, when net for air-source heat pump units 1000 is in uninterruptedly provide low-temperature receiver simultaneously, when thermal source or domestic hot-water's output mode, the 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, the first cross valve 40a, the second cross valve 40b, the 3rd cross valve 40c and the 4th cross valve 40d be the state in the 5th valve port g and the 8th valve port j conducting and 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 shown in the arrow 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 flow through check-valves 100 enter into refrigeration restricting element 130 in, refrigerant enters in falling film type heat exchanger 120 after reducing pressure by regulating flow in refrigeration restricting element 130, refrigerant becomes gas after absorbing heat in falling film type heat exchanger 120 and evaporating, gas coolant is sucked by compressor 10 by the connecting line between falling film type heat exchanger 120 and compressor 10 and air entry b, refrigerant is again discharged after compression in compressor 10, form kind of refrigeration cycle.
Due to refrigerant release heat in shell and tube exchanger 90, thereby can be at the m place, the first row mouth of a river of shell and tube exchanger 90 to using side that thermal source or domestic hot-water are provided, in the time 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.
Due to the refrigerant evaporation of absorbing heat in falling film type heat exchanger 120, thus can be at the n place, the second row mouth of a river of falling film type heat exchanger 120 to using side that low-temperature receiver is provided.Net for air-source heat pump units 1000 can provide thermal source and low-temperature receiver simultaneously thus, and thermal source and low-temperature receiver can be utilized simultaneously, and without release heat in finned heat exchanger or absorption heat, it is maximum that the using energy source of net for air-source heat pump units 1000 reaches.
As shown in Figure 2, when net for air-source heat pump units 1000 is in meeting low-temperature receiver demand but while also needing to continue to provide the non-stop run of thermal source to regulate pattern, the 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, the first cross valve 40a, the second cross valve 40b, the 3rd cross valve 40c and the 4th cross valve 40d be the state in the 5th valve port g and the 8th valve port j conducting and 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 shown in the arrow 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 becomes after release heat as liquid in shell and tube exchanger 90, flow through check-valves 100 and control valve 110 of liquid coolant enters in common line 80, refrigerant in common line 80 heats restricting element 70a through first respectively, second heats restricting element 70b, the 3rd enters into the first finned heat exchanger 30a after heating the reducing pressure by regulating flow that restricting element 70c and the 4th heats restricting element 70d, the second finned heat exchanger 30b, in the 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, the refrigerant flowing out from four-way change-over valve 20 is compressed rear discharge being sucked by compressor 10 again, form heat pump cycle.Now, due to refrigerant release heat in shell and tube exchanger 90, can provide thermal source or domestic hot-water to use side at the m place, the first row mouth of a river of shell and tube exchanger 90 thus.
As shown in Figure 3, when net for air-source heat pump units 1000 is in meeting thermal source demand but while also needing to continue to provide the non-stop run of low-temperature receiver to regulate pattern, the 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, the first cross valve 40a, the second cross valve 40b, the 3rd cross valve 40c and the 4th cross valve 40d be the state in the 5th valve port g and the 8th valve port j conducting and 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 shown in the arrow in Fig. 3, the gas coolant of the HTHP of discharging from the exhaust outlet a of compressor 10 after four-way change-over valve 20 respectively the 7th valve port i from four cross valves enter in four cross valves, the refrigerant entering in each cross valve enters in corresponding finned heat exchanger through the 6th valve port h, after entering into four refrigerant release heat in finned heat exchanger, become as liquid, 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 type heat exchanger 120, refrigerant is discharged after the interior heat absorption evaporation of falling film type heat exchanger 120 becomes as gas, the refrigerant of discharging from falling film type heat exchanger 120 is discharged after again compressing after being sucked by compressor 10 through the connecting line between falling film type heat exchanger 120 and compressor 10, forms kind of refrigeration cycle.Due to the refrigerant evaporation of absorbing heat in falling film type heat exchanger 120, thus can be at the n place, the second row mouth of a river of falling film type heat exchanger 120 to using side that low-temperature receiver is provided.
As shown in Figure 4, when net for air-source heat pump units 1000 is in single when thermal source being provided and the 4th finned heat exchanger 30d being defrosted, the 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, the 4th cross valve 40d commutates and makes 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 of the 4th cross valve 40d, the first cross valve 40a, the second cross valve 40b, the 3rd cross valve 40c still keeps the state of the 5th valve port g and the 8th valve port j conducting and 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 in the arrow in Fig. 4, the high temperature and high pressure gas refrigerant of discharging from the exhaust outlet a of compressor 10 is divided into two-way circulation, wherein a road enters into shell and tube exchanger 90 through four-way change-over valve 20, and this road refrigerant becomes after release heat and enters into common line 80 for liquid and flow through check-valves 100 and control valve 110 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 becomes as liquid after release heat in the 4th finned heat exchanger 30d, utilize the heat that refrigerant discharges that the frost layer on the 4th finned heat exchanger 30d surface is melted, 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 of the control valve 110 of flowing through.Refrigerant after converging is flowed through respectively and first is heated 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, the 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 enters in four-way change-over valve 20 by the first cross valve 40a, the second cross valve 40b and the 3rd cross valve 40c respectively and sucked by compressor 10.The refrigerant being sucked by compressor 10 is compressed rear discharge again, forms heat pump cycle.Now, due to cold-producing medium release heat in shell and tube exchanger 90, therefore can provide thermal source or domestic hot-water to use side at the first row mouth of a river of shell and tube exchanger 90 m.
As shown in Figure 5, when net for air-source heat pump units 1000 is in single when thermal source being provided and the 3rd finned heat exchanger 30c being defrosted, the 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, the 3rd cross valve 40c commutates and makes 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 of the 3rd cross valve 40c, the first cross valve 40a, the second cross valve 40b, the 4th cross valve 40d still keeps the state of the 5th valve port g and the 8th valve port j conducting and 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 in the arrow in Fig. 5, the high temperature and high pressure gas refrigerant of discharging from the exhaust outlet a of compressor 10 is divided into two-way circulation, wherein a road enters into shell and tube exchanger 90 through four-way change-over valve 20, and this road refrigerant becomes after release heat and enters into common line 80 for liquid and flow through check-valves 100 and control valve 110 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 becomes as liquid after release heat in the 3rd finned heat exchanger 30c, utilize the heat that refrigerant discharges that the frost layer on the 3rd finned heat exchanger 30c surface is melted, 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 of the control valve 110 of flowing through.Refrigerant after converging is flowed through respectively and first is heated 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, the 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 enters in four-way change-over valve 20 by the first cross valve 40a, the second cross valve 40b and the 4th cross valve 40d respectively and sucked by compressor 10.The refrigerant being sucked by compressor 10 is compressed rear discharge again, forms heat pump cycle.Now, due to cold-producing medium release heat in shell and tube exchanger 90, therefore can provide thermal source or domestic hot-water to use side at the first row mouth of a river of shell and tube exchanger 90 m.
As shown in Figure 6, when net for air-source heat pump units 1000 is in single when thermal source being provided and the second finned heat exchanger 30b being defrosted, the 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, the second cross valve 40b commutates and makes 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 of the second cross valve 40b, the first cross valve 40a, the 3rd cross valve 40c, the 4th cross valve 40d still keeps the state of the 5th valve port g and the 8th valve port j conducting and 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 in the arrow 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 circulation, wherein a road enters into shell and tube exchanger 90 through four-way change-over valve 20, and this road refrigerant becomes after release heat and enters into common line 80 for liquid and flow through check-valves 100 and control valve 110 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 becomes as liquid after release heat in the second finned heat exchanger 30b, utilize the heat that refrigerant discharges that the frost layer on the second finned heat exchanger 30b surface is melted, 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 of the control valve 110 of flowing through.Refrigerant after converging is flowed through respectively and first is heated 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, the 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 enters in four-way change-over valve 20 by the first cross valve 40a, the 3rd cross valve 40c and the 4th cross valve 40d respectively and sucked by compressor 10.The refrigerant being sucked by compressor 10 is compressed rear discharge again, forms heat pump cycle.Now, due to cold-producing medium release heat in shell and tube exchanger 90, therefore can provide thermal source or domestic hot-water to use side at the first row mouth of a river of shell and tube exchanger 90 m.
As shown in Figure 7, when net for air-source heat pump units 1000 is in single when thermal source being provided and the first finned heat exchanger 30a being defrosted, the 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, the first cross valve 40a commutates and makes 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 of the first cross valve 40a, the second cross valve 40b, the 3rd cross valve 40c, the 4th cross valve 40d still keeps the state of the 5th valve port g and the 8th valve port j conducting and 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 in the arrow in Fig. 7, the high temperature and high pressure gas refrigerant of discharging from the exhaust outlet a of compressor 10 is divided into two-way circulation, wherein a road enters into shell and tube exchanger 90 through four-way change-over valve 20, and this road refrigerant becomes after release heat and enters into common line 80 for liquid and flow through check-valves 100 and control valve 110 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 becomes as liquid after release heat in the first finned heat exchanger 30a, utilize the heat that refrigerant discharges that the frost layer on the first finned heat exchanger 30a surface is melted, 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 of the control valve 110 of flowing through.Refrigerant after converging is flowed through respectively and second is heated 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, the 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 enters in four-way change-over valve 20 by the second cross valve 40b, the 3rd cross valve 40c and the 4th cross valve 40d respectively and sucked by compressor 10.The refrigerant being sucked by compressor 10 is compressed rear discharge again, forms heat pump cycle.Now, due to cold-producing medium release heat in shell and tube exchanger 90, therefore can provide thermal source or domestic hot-water to use side at the first row mouth of a river of shell and tube exchanger 90 m.
Wherein, it should be noted that, four cross valves work independently, non-interference between four cross valves, above-mentioned description is the illustrating of refrigerant circulation of the net for air-source heat pump units 1000 need defrost to a finned heat exchanger time, and what be worth understanding is, the utility model is not limited to this,, can defrost to two or three finned heat exchangers during in heating operation in net for air-source heat pump units 1000 simultaneously, also can carry out circulating defrosting in turn to four finned heat exchangers.The finned heat exchanger wherein defrosting can be combined to carry out the defrost process of sequencing.
According to the net for air-source heat pump units 1000 of the utility model embodiment, by being provided with multiple finned heat exchangers, multiple cross valve, shell and tube exchanger 90 and falling film type heat exchanger 120, thereby not only can be uninterruptedly simultaneously to using side that low-temperature receiver and thermal source or domestic hot-water are provided, 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 be by provide the pattern seamless switching of low-temperature receiver and thermal source for the pattern of single low-temperature receiver or thermal source is provided simultaneously.And can defrost to finned heat exchanger in the winter time according to the net for air-source heat pump units 1000 of the utility model embodiment time, uninterruptedly provide thermal source, avoiding traditional reduces because of the finned heat exchanger impatient acute comfortableness of bringing that declines of use side temperature cycle causing that defrosts, improve user's comfort, and heating operation is continual and steady during defrosting, do not cause that system pressure changes, therefore compressor 10 is not impacted, extended the service life of compressor 10.
As shown in Fig. 1-Fig. 7, in specific embodiments more of the present utility model, the 5th valve port g of multiple cross valves is communicated with by first passage 150, and first passage 150 is connected with exhaust outlet a.That is to say, the 5th valve port g of the first cross valve 40a, the 5th valve port g of the 5th valve port g of the second cross valve 40b, the 3rd cross valve 40c and the 5th valve port g of the 4th cross valve 40d are communicated with by first passage 150.Thereby make the simple in structure of net for air-source heat pump units 1000.
According to embodiment more of the present utility model, as shown in Fig. 1-Fig. 7, the 7th valve port i of multiple cross valves 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 to say, the 7th valve port i of the first cross valve 40a, the 7th valve port i of the 7th valve port i of the second cross valve 40b, the 3rd cross valve 40c and the 7th valve port i of the 4th cross valve 40d are communicated with by second channel 160.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 that the 8th valve port j of the 3rd cross valve 40c is connected to second channel 160, the four cross valve 40d by first throttle element 50 is connected to second channel 160 by first throttle element 50.Thereby make the simple in structure of net for air-source heat pump units 1000.
In the description of this description, the description of reference term " embodiment ", " some embodiment ", " illustrative examples ", " example ", " concrete example " or " some examples " etc. means to be contained at least one embodiment of the present utility model or example in conjunction with specific features, structure, material or the feature of this embodiment or example description.In this manual, the schematic statement of above-mentioned term is not necessarily referred to identical embodiment or example.And specific features, structure, material or the feature of description can be with suitable mode combination in any one or more embodiment or example.
Although illustrated and described embodiment of the present utility model, those having ordinary skill in the art will appreciate that: in the situation that not departing from principle of the present utility model and aim, can carry out multiple variation, amendment, replacement and modification to these embodiment, scope of the present utility model is limited by claim and equivalent 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 the first valve port is connected with described exhaust outlet, and described the second valve port is connected with described air entry;
Multiple finned heat exchangers and multiple cross valve, described multiple finned heat exchanger and described multiple cross valve are corresponding one by one, each described cross valve comprises the 5th to the 8th valve port, described the 5th valve port of each described cross valve is connected with described exhaust outlet, described the 6th valve port of each described cross valve is connected with one end of corresponding described finned heat exchanger, described the 7th valve port of each described cross valve is connected with described the 3rd valve port, described the 8th valve port of each described cross valve is connected with described the 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 the 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 type heat exchanger, described falling film type 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 outlet is connected with described refrigeration restricting element.
2. net for air-source heat pump units according to claim 1, is characterized in that, described the 5th valve port of described multiple cross valves 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 the 7th valve port of described multiple cross valves is communicated with by second channel, and described the 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 the 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.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201320816554.XU CN203785316U (en) | 2013-12-11 | 2013-12-11 | Air source heat pump unit |
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| Application Number | Priority Date | Filing Date | Title |
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| CN201320816554.XU CN203785316U (en) | 2013-12-11 | 2013-12-11 | Air source heat pump unit |
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| CN203785316U true CN203785316U (en) | 2014-08-20 |
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Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104266407A (en) * | 2014-10-21 | 2015-01-07 | 王仕相 | Air source heat pump unit |
| CN104713264A (en) * | 2013-12-11 | 2015-06-17 | 重庆美的通用制冷设备有限公司 | Air source heat pump set |
-
2013
- 2013-12-11 CN CN201320816554.XU patent/CN203785316U/en not_active Withdrawn - After Issue
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104713264A (en) * | 2013-12-11 | 2015-06-17 | 重庆美的通用制冷设备有限公司 | Air source heat pump set |
| CN104713264B (en) * | 2013-12-11 | 2017-05-03 | 重庆美的通用制冷设备有限公司 | Air source heat pump set |
| CN104266407A (en) * | 2014-10-21 | 2015-01-07 | 王仕相 | Air source heat pump unit |
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