CN207763308U - A kind of parallel connection Cascade type heat pump system - Google Patents
A kind of parallel connection Cascade type heat pump system Download PDFInfo
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- CN207763308U CN207763308U CN201721921252.3U CN201721921252U CN207763308U CN 207763308 U CN207763308 U CN 207763308U CN 201721921252 U CN201721921252 U CN 201721921252U CN 207763308 U CN207763308 U CN 207763308U
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Abstract
The utility model is related to art of heat pumps, disclose a kind of Cascade type heat pump system in parallel, including a plurality of defrosting/heating branch, it is sequentially connected in series to form defrosting/heating circulation loop with first direction control valve, heat exchanger assembly, second direction control valve after a plurality of defrosting/heating branch circuit parallel connection, the defrosting/heating branch includes the compressor being sequentially connected in series, heat exchanger and pattern switching component.The utility model provides a kind of Cascade type heat pump system in parallel, when heat pump being enabled to be defrosted, can guarantee the cold medium flux for flowing into evaporator and improves the defrosting efficiency of evaporator.
Description
Technical field
The utility model is related to art of heat pumps, are specifically related to a kind of Cascade type heat pump system in parallel.
Background technology
Conventional heat pump unit parallel system refrigerant is first in parallel after compressor outflow, then is diverted to two wings by triple valve
In plate heat interchanger, when Defrost operation, since the finned heat exchanger in two systems cannot accomplish striking resemblances, to its frosting
Degree is different, and when Defrost operation, since the frosting degree of two finned heat exchangers is different, it is finned that refrigerant by threeway flows into two
The flow of heat exchanger also can be different, and the more serious finned heat exchanger of frosting degree, refrigerant flow through the more serious fin of frosting and change
The coolant quantity of hot device is fewer, and longer so as to cause the more serious finned heat exchanger defrosting time of frosting, defrosting efficiency is lower.
Utility model content
For the technical problems in the prior art, the purpose of this utility model is：A kind of superposition type heat in parallel is provided
Pumping system so that when heat pump is defrosted, the cold medium flux for flowing into evaporator is can guarantee, to improve the defrosting effect of evaporator
Rate.
To achieve the goals above, the utility model provides a kind of Cascade type heat pump system in parallel, including a plurality of defrosting/system
Hot branch, after a plurality of defrosting/heating branch circuit parallel connection with first direction control valve, heat exchanger assembly, second direction control valve
It is sequentially connected in series to form defrosting/heating circulation loop；
The defrosting/heating branch includes the compressor being sequentially connected in series, heat exchanger and pattern switching component.
Preferably, the defrosting/heating branch is set as two, is followed successively by the first defrosting/heating branch and second
Defrosting/heating branch；
First defrosting/heating branch includes the first compressor, First Heat Exchanger and the first mould being sequentially connected in series
Formula changeover module；
Second defrosting/heating branch includes the second compressor, the second heat exchanger and the second mould being sequentially connected in series
Formula changeover module.
Preferably, the first direction control valve is the first triple valve, and first triple valve is equipped with first end
The first port of mouth, second port and the third port for being located at described second port the same side, first triple valve connects institute
Heat exchanger group is stated, the second port of first triple valve is connect with the first mode changeover module, first threeway
The third port of valve is connect with the second mode changeover module.
Preferably, the second direction control valve is the second triple valve, and second triple valve is equipped with first end
Mouthful, second port and the third port for being located at described second port the same side, the first port of second triple valve with it is described
Heat exchanger group connects, and the second port of second triple valve is connect with the gas returning port of first compressor, and described second
The third port of triple valve is connect with the gas returning port of second compressor.
Preferably, each pattern switching component includes two expansion valves being connected in parallel with each other, the heat
Pump switches the different expansion valves in the case where carrying out heating mode or defrosting mode.
Preferably, the first mode changeover module includes the first check valve, the first electric expansion valve and first
Heating power expansion valve, first check valve are connected in series with rear and first heating power expansion valve simultaneously with first electric expansion valve
Connection connection；
The second mode changeover module includes the second check valve, the second electric expansion valve and the second heating power expansion valve, institute
It states after the second check valve is connected in series with second electric expansion valve and is connected in parallel with second heating power expansion valve.
Preferably, in defrosting mode, refrigerant passes sequentially through first compressor, First Heat Exchanger, first
Check valve, the first electric expansion valve, the first triple valve and heat exchanger group connect to form the first defrosting circulation loop；
In heating mode, it is swollen that refrigerant passes sequentially through the first compressor, heat exchanger group, the first triple valve, the first heating power
Swollen valve, First Heat Exchanger and the first compressor connect to form the first heating circulation loop；
In defrosting mode, it is swollen that refrigerant passes sequentially through the second compressor, the second heat exchanger, the second check valve, the second electronics
Swollen valve, the first triple valve and heat exchanger group connect to form the second defrosting circulation loop；
In heating mode, it is swollen that refrigerant passes sequentially through the second compressor, heat exchanger group, the first triple valve, the second heating power
Swollen valve, the second heat exchanger and the second compressor connect to form the second heating circulation loop.
Preferably, in the defrosting circulation loop, the heat exchanger group includes third heat exchanger, the 4th changes
Hot device, the 5th heat exchanger, the 6th heat exchanger and the 7th heat exchanger, the third heat exchanger connect with the first direction control valve
It connects, the third heat exchanger is connect by third triple valve with the 4th heat exchanger and the 5th heat exchanger, the 4th heat exchange
Device is connect with six heat exchanger, and the 5th heat exchanger is connect with the 7th heat exchanger, the 6th heat exchanger and the 7th
Heat exchanger is connected by the second direction control valve.
Preferably, the third heat exchanger has six ports a, b, c, d, e and f, a of the third heat exchanger
Mouth is connect with the air injection enthalpy-increasing mouth of second compressor, the jet of the b mouths and first compressor of the third heat exchanger
Increasing enthalpy mouth connects, and the c mouths of the third heat exchanger are connect with the first port of the third triple valve, the third heat exchanger
D, it is connect with the first port of first triple valve for e and f mouthfuls.
Preferably, further include the first four-way valve and the second four-way valve, the S mouths of first four-way valve and described the
The gas returning port of one compressor connects, and the E mouths of first four-way valve are connect with the First Heat Exchanger, first four-way valve
C mouthfuls connect with the 6th heat exchanger, and the D mouths of first four-way valve are connect with the exhaust outlet of first compressor；
The S mouths of second four-way valve are connect with the gas returning port of second compressor, the E mouths of second four-way valve with
The second heat exchanger connection, the C mouths of second four-way valve are connect with the 7th heat exchanger, the D of second four-way valve
Mouth is connect with the exhaust outlet of second compressor.
A kind of Cascade type heat pump system in parallel that the utility model embodiment is provided, has the following technical effect that：
The Cascade type heat pump system in parallel of the present embodiment, including a plurality of defrosting/heating branch, a plurality of defrosting/heating branch
It is sequentially connected in series to form defrosting/heating cycle with first direction control valve, heat exchanger assembly, second direction control valve after parallel connection
Circuit, defrosting/heating branch include the compressor being sequentially connected in series, heat exchanger and pattern switching component, therefore, every circulation branch road
In compressor caused by refrigerant all flow in heat exchanger connected to it, so that heat exchanger defrosts, in addition, existing
There is a compressor in technology to be connected in series with multiple heat exchangers, the refrigerant in compressor is branched to again in each heat exchanger, by
Different in the frosting degree of each heat exchanger, the refrigerant generated by a compressor cannot be according to the frosting degree of heat exchanger point
It is assigned in each heat exchanger, to cause heat exchanger that can defrost halfway problem, is based on the technical program, carried out in heat pump
When defrosting, the cold medium flux for flowing into evaporator is can guarantee, to improve the defrosting efficiency of evaporator.
In addition, in the both ends setting first direction control valve and second direction control valve of defrosting circulation branch road, first direction
Multiple ports are arranged in one end that control valve is connect with defrosting circulation branch road, and an end is arranged in the other end of first direction control valve
Mouthful, therefore first shunted before refrigerant enters first direction control valve, into first direction control valve after in cocurrent；Second direction control
Multiple ports are arranged in one end that valve processed is connect with defrosting circulation branch road, and a port is arranged in the other end of second direction control valve,
Therefore first collaborate before refrigerant enters second direction control valve, into first direction control valve after shunting, therefore, pass through setting
First direction control valve and second direction control valve, can reduce the setting of pipeline in heat pump, simplify system.
Description of the drawings
Fig. 1 is a kind of system construction drawing of Cascade type heat pump system in parallel of the utility model；
Fig. 2 is the signal of the First Heat Exchanger and the second heat exchanger of a kind of Cascade type heat pump system in parallel of the utility model
Figure；
Fig. 3 is the first compressor, the second compressor, third pressure of a kind of Cascade type heat pump system in parallel of the utility model
The schematic diagram of contracting machine and the 4th compressor；
Fig. 4 changes for a kind of the 6th heat exchanger of Cascade type heat pump system in parallel of the utility model, the 7th heat exchanger, the 8th
The schematic diagram of hot device and the 9th heat exchanger；
Fig. 5 is the signal of the first four-way valve and the second four-way valve of a kind of Cascade type heat pump system in parallel of the utility model
Figure；
Fig. 6 is a kind of schematic diagram of the third heat exchanger of Cascade type heat pump system in parallel of the utility model；
Fig. 7 is a kind of signal of the 4th heat exchanger and the 5th heat exchanger of Cascade type heat pump system in parallel of the utility model
Figure；
Fig. 8 is the first triple valve, the second triple valve and the third of a kind of Cascade type heat pump system in parallel of the utility model
The schematic diagram of triple valve.
1, First Heat Exchanger；2, the second heat exchanger；3, first mode changeover module；31, the first electric expansion valve；32,
One check valve；33, the first heating power expansion valve；4, second mode changeover module；41, the second electric expansion valve；42, second is unidirectional
Valve；43, the second heating power expansion valve；5, the first four-way valve；6, the second four-way valve；7, the first compressor；8, the second compressor；9,
One triple valve；10, the second triple valve；11, third triple valve；12, third heat exchanger；13, the 4th heat exchanger；14, the 5th heat exchange
Device；15, third compressor；16, the 4th compressor；17, first throttling device；18, second throttling device；19, the tenth heat exchange
Device；20, the 11st heat exchanger；21, the 6th heat exchanger；22, the 7th heat exchanger；23, the 8th heat exchanger；24, the 9th heat exchanger.
Specific implementation mode
With reference to the accompanying drawings and examples, specific embodiment of the present utility model is described in further detail.Below
Embodiment is not intended to limit the scope of the present invention for illustrating the utility model.
As shown in Figure 1, a kind of parallel connection Cascade type heat pump system, a plurality of defrosting/heating branch, a plurality of defrosting/heating branch
It is sequentially connected in series with first direction control valve, heat exchanger assembly, second direction control valve after the parallel connection of road and to form defrosting/heating and follow
Loop back path；
Defrosting/heating branch includes the compressor being sequentially connected in series, heat exchanger and pattern switching component.
Based on above-mentioned setting, the Cascade type heat pump system in parallel of the present embodiment, including a plurality of defrosting/heating branch, it is a plurality of
It is sequentially connected in series and to be formed with first direction control valve, heat exchanger assembly, second direction control valve after defrosting/heating branch circuit parallel connection
Defrosting/heating circulation loop, defrosting/heating branch include the compressor being sequentially connected in series, heat exchanger and pattern switching component, because
This, refrigerant caused by the compressor in every circulation branch road is all flow in heat exchanger connected to it, for heat exchanger into
Row defrosting, in addition, a compressor is connected in series with multiple heat exchangers in the prior art, the refrigerant in compressor branches to again
In each heat exchanger, since the frosting degree of each heat exchanger is different, the refrigerant that is generated by a compressor cannot be according to changing
The frosting degree of hot device is distributed into each heat exchanger, to cause heat exchanger that can defrost halfway problem, is based on this skill
Art scheme can guarantee the cold medium flux for flowing into evaporator, to improve the defrosting efficiency of evaporator when heat pump is defrosted.
In addition, in the both ends setting first direction control valve and second direction control valve of defrosting circulation branch road, first direction
Multiple ports are arranged in one end that control valve is connect with defrosting circulation branch road, and an end is arranged in the other end of first direction control valve
Mouthful, therefore first shunted before refrigerant enters first direction control valve, into first direction control valve after in cocurrent；Second direction control
Multiple ports are arranged in one end that valve processed is connect with defrosting circulation branch road, and a port is arranged in the other end of second direction control valve,
Therefore first collaborate before refrigerant enters second direction control valve, into first direction control valve after shunting, therefore, pass through setting
First direction control valve and second direction control valve, can reduce the setting of pipeline in heat pump, simplify system.
In the present embodiment, as shown in Figure 1, defrosting/heating branch is set as two, it is the first defrosting/heating branch and second
Defrosting/heating branch；First defrosting/heating branch includes the first compressor 7 being sequentially connected in series, First Heat Exchanger 1 and
One pattern switching component 3；Second defrosting/heating branch includes the second compressor 8 being sequentially connected in series, 2 and of the second heat exchanger
Second mode changeover module 4, wherein First Heat Exchanger 1 is under heating mode and defrosting mode respectively as evaporator and condensation
Device, the second heat exchanger 2 pass through setting first under heating mode and defrosting mode respectively as evaporator and condenser, this programme
The circulation branch road that defrosts and the second defrosting circulation branch road, the refrigerant that the first compressor 7 in the first defrosting circulation branch road generates are whole
It is flow to First Heat Exchanger 1, the refrigerant that the second compressor 8 in the second defrosting circulation branch road generates all flow to the second heat exchanger 2,
Therefore, in the circulation branch road that defrosts at every, refrigerant caused by each compressor can all be flow in its corresponding heat exchanger, be carried
Its high defrosting efficiency；
Each mode switch element includes two expansion valves being connected in parallel with each other, and heat pump is carrying out heating mode or removing
Switch different expansion valves under white pattern, mode switch element plays the role of throttling, to which mode switch element is mainly pair
Carry out refrigerant to be depressured, and then ensure the flow of refrigerant when defrosting, realizes quickly defrosting, improve the efficiency of defrosting.
In the present embodiment, as shown in figs. 1 and 8, first direction control valve is the first triple valve 9, and the first triple valve 9 is equipped with the
Single port, second port and the third port for being located at second port the same side, if first port, the second end of the first triple valve 9
Mouthful and third port be respectively a mouths of the first triple valve, b mouthfuls and c mouthfuls, a mouths of the first triple valve 9 are connected with heat exchanger group,
The b mouths of first triple valve 9 are connect with first mode changeover module 3, c mouths and the second mode changeover module 4 of the first triple valve 9
Connection, thus, refrigerant enter the first triple valve 9 before be shunting, diverter branch be respectively first circulation branch and
Second circulation branch, flow through first circulation branch and second circulation branch refrigerant flow into b mouths of the first triple valve 9 with c mouthfuls after,
It is flowed out again from a mouths of the first triple valve 9, therefore, refrigerant divides before entering the first triple valve 9 and after entering the first triple valve 9
It is not shunting and interflow to reduce the setting of pipeline in heat pump by the way that the first triple valve 9 is arranged, simplify system.
In the present embodiment, as shown in figs. 1 and 8, second direction control valve is the second triple valve 10, and the second triple valve 10 is set
There are first port, second port and the third port for being located at second port the same side, if the first port of the second triple valve 10,
Two-port netwerk and third port be respectively a mouths of the second triple valve 10, b mouthfuls and c mouthfuls, a mouths and heat exchanger of the second triple valve 10
Group connection, the b mouths of the second triple valve 10 are connect with the gas returning port of the first compressor 7, the c mouths of the second triple valve 10 and the second compression
The gas returning port of machine 8 connects, and similarly, refrigerant is shunting before entering the second triple valve 10, and diverter branch is respectively first
Circulation branch road and second circulation branch, the refrigerant for flowing through first circulation branch and second circulation branch flow into the second triple valve 10
The return-air of b mouths and c mouthfuls of gas returning ports for being back to the first compressor 7 and the second compressor 8 after a mouthfuls, then from the first triple valve 9
Mouthful, therefore, refrigerant is interflow and shunting respectively, passes through setting before entering the first triple valve 9 and after entering the first triple valve 9
Second triple valve 10, can reduce the setting of pipeline in heat pump, simplify system.
In the present embodiment, as shown in Figure 1, first mode changeover module 3 includes the first check valve 32, the first electronic expansion
Valve 31 and the first heating power expansion valve 33, the first check valve 31 and the first electric expansion valve 31 are connected in series with rear and the first thermal expansion
Valve 33 is connected in parallel；
Second mode changeover module 4 includes the second check valve 42, the second electric expansion valve 41 and the second heating power expansion valve 43,
Second check valve 42 is connected in parallel after being connected in series with the second electric expansion valve 41 with the second heating power expansion valve 43；
Thus, each pattern switching component is by being arranged two distinct types of expansion valve, respectively thermal expansion
Valve and electric expansion valve, since thermal expansion valve opening is limited by temperature and pressure, when in low temperature, heating power expansion valve is not
It can be in maximum opening, the flow of refrigerant when limiting defrosting, and the aperture regulation range of electric expansion valve is big, not by temperature
Influence, the aperture of electric expansion valve can be transferred to as needed it is maximum or minimum, it is long to avoid heat pump from defrosting time occur,
And the sordid phenomenon of defrosting；Heating power expansion valve uses under high ambient temperatures, and efficiency is higher, therefore, according to different
Operating mode selects different expansion valves to work, so as to improve working efficiency；
By the way that first mode changeover module 3 and second mode changeover module 4 is arranged, under different working modes, change
The flow direction of refrigerant makes refrigerant flow to corresponding throttling set, while to being cut by first mode changeover module 3 and second mode
The refrigerant for changing component 4 is depressured, and the reliability of heat pump product is improved.
In the present embodiment, as shown in Figure 1, in defrosting mode, refrigerant passes sequentially through first compressor 7, first changes
Hot device 1, the first check valve 32, the first electric expansion valve 31, the first triple valve 9 are connected with heat exchanger group to be formed the first defrosting and follows
Loop back path；
In heating mode, refrigerant passes sequentially through the first compressor 7, heat exchanger group, the first triple valve 9, the first heating power
Expansion valve 33, First Heat Exchanger 1 and the connection of the first compressor 7 form the first heating circulation loop；
In defrosting mode, refrigerant passes sequentially through the second compressor 8, the second heat exchanger 2, second the 42, second electricity of check valve
Sub- expansion valve 41, the first triple valve 9 connect to form the second defrosting circulation loop with heat exchanger group；
In heating mode, refrigerant passes sequentially through the second compressor 8, heat exchanger group, the first triple valve 9, the second heating power
Expansion valve 43, the second heat exchanger 2 and the connection of the second compressor 8 form the second heating circulation loop；
In defrosting, refrigerant flows through the first electric expansion valve 31 or the second electric expansion valve 41, the first electric expansion valve
31 or second electric expansion valve 41 be used as throttling set, play the role of throttling；
When being heated, refrigerant is swollen by the first heating power expansion valve 33 or the second heating power expansion valve 43, the first heating power
Swollen valve 33 or the second heating power expansion valve 43 are used as throttling set, play the role of throttling.
In the present embodiment, as shown in Fig. 1,4,6 and 7, in the circulation loop that defrosts, second heat exchanger group includes that third is changed
Hot device 12, the 4th heat exchanger 13, the 5th heat exchanger 14, the 6th heat exchanger 21, the 7th heat exchanger 22, the 8th heat exchanger the 23, the 9th
Heat exchanger 24, the tenth heat exchanger 19 and the 11st heat exchanger 20, third heat exchanger 12 are the increasing enthalpy heat exchanger with 6 interfaces,
Its six interfaces are respectively a, b, c, d, e and f mouthfuls；4th heat exchanger 13 and the 5th heat exchanger 14 are board-like with 4 interfaces
Heat exchanger, four interfaces are respectively a, b, c and d mouthfuls；6th heat exchanger 21, the 7th heat exchanger 22, the 8th heat exchanger 23 and
Nine heat exchangers 24 are the heat exchanger with 6 interfaces, and six interfaces are respectively a, b, c, d, e and f mouthfuls；Tenth heat exchanger 19
It is the increasing enthalpy heat exchanger with 4 interfaces with the 11st heat exchanger 20, four interfaces are respectively a, b, c and d mouthfuls；
4th heat exchanger 13 and the 5th heat exchanger 14 are plate heat exchanger, the 6th heat exchanger 21, the 7th heat exchanger the 22, the 8th
Heat exchanger 23 and the 9th heat exchanger 24 are double-tube heat exchanger, and the tenth heat exchanger 19 and the 11st heat exchanger 20 are increasing enthalpy heat exchanger；
A, b, c mouth of third heat exchanger 12 are connect with first direction control valve, i.e., connect with the first triple valve 9, then flow
The refrigerant for entering third heat exchanger 12 is flowed out by the c mouths of third heat exchanger 12, and the refrigerant being then out passes through the second triple valve 10
It is connect with a mouths of a mouths of the 4th heat exchanger 13 and the 5th heat exchanger 14, c mouths and the 6th heat exchanger 21 of the 4th heat exchanger 13
The connection of e mouths, the c mouths of the 5th heat exchanger 14 connect with a mouths of the 7th heat exchanger 22, and a mouths and the 7th of the 6th heat exchanger 21 change
The e mouths of hot device are connected by second direction control valve, i.e., by a mouths of the second triple valve connect, d mouths of the tenth heat exchanger 19 and
The a mouths of 8th heat exchanger 23 connect, and the d mouths of the 11st heat exchanger 20 are connect with a mouths of the 9th heat exchanger 24；Thus, logical
It crosses in the second heat exchange group and multiple heat exchangers is set, different heat exchangers is attached, so that heat pump has a variety of work
Pattern improves its working efficiency.
In the present embodiment, as shown in figs. 1 and 8, set between third heat exchanger 12 and the 4th heat exchanger 13, the 5th heat exchanger 14
It is equipped with third triple valve 11, the first port (a mouthfuls) of third triple valve 11 is located at the side of third heat exchanger 12, the second threeway
It the second port (b mouthfuls) of valve 10 and is located at the 4th heat exchanger 13 and the 5th with the third port (c mouthfuls) of second port the same side and changes
The side of hot device 14, wherein the first port, second port and third port for setting third triple valve 11 are respectively a mouthfuls, b mouthfuls and c
Mouthful, by the way that third triple valve 11 is arranged, the refrigerant flowed out from third heat exchanger 12 can be made to pass through the second end of third triple valve 11
Mouth (b mouthfuls) and third port (c mouthfuls), are that two articles of different pipelines flow to the 4th heat exchanger 13 and the 5th heat exchanger 14 respectively
In, have the function of changing the flow direction of refrigerant.
In the present embodiment, as shown in figs. 1 and 6, third heat exchanger 12 is the first increasing enthalpy heat exchanger, the energy saving height of increasing enthalpy heat exchanger
Effect, and the first increasing enthalpy heat exchanger is connect with compressor, can increase the capacity of compressor.
In the present embodiment, as shown in figs. 1 and 6, the first increasing enthalpy heat exchanger have six ports a, b, c, d, e and f, first
The a mouths of increasing enthalpy heat exchanger are connect with the air injection enthalpy-increasing mouth of the second compressor 8, b mouths and the first compressor 7 of the first increasing enthalpy heat exchanger
The connection of air injection enthalpy-increasing mouth, c mouths of the first increasing enthalpy heat exchanger connect with the first port (a mouthfuls) of third triple valve 11, the first increasing
D, e and f mouth of enthalpy heat exchanger are connect with the first port (a mouthfuls) of the first triple valve 9；Thus, by being located at third heat exchange
Multiple interfaces of device 12, third heat exchanger 12 and the first compressor 7, the second compressor 8, the first triple valve 9, the 4th heat exchanger 13
It connects, is connect with other workpieces to avoid being arranged multiple third heat exchangers 12 so that heat pump system with the 5th heat exchanger 14
System is more simplified, working efficiency higher.
In the present embodiment, as described in figures 1 and 5, Cascade type heat pump system in parallel further includes the first four-way valve 5 and the second four-way
The S mouths of valve 6, the first four-way valve 5 are connect with the gas returning port of the first compressor 7, and E mouths and the First Heat Exchanger 1 of the first four-way valve 5 connect
It connects, the C mouths of the first four-way valve 5 are connect with the 6th heat exchanger 21, the exhaust outlet of the D mouths and the first compressor 7 of the first four-way valve 5
Connection；
The S mouths of second four-way valve 6 are connect with the gas returning port of the second compressor 8, the E mouths of the second four-way valve 6 and the second heat exchange
Device 2 connects, and the C mouths of the second four-way valve 6 are connect with the 7th heat exchanger 22, the row of the D mouths and the second compressor 8 of the second four-way valve 6
Gas port connects；
By the way that the first four-way valve 5 and the second four-way valve 6 are arranged in Cascade type heat pump system in parallel, change to realize
The flow direction of refrigerant in system realizes defrosting or the switching of heat-production functions.
In the present embodiment, as illustrated in fig. 1 and 2, First Heat Exchanger 1 and the second heat exchanger 2 are finned heat exchanger, fin heat exchange
The heat transfer efficiency of device is high, and compact-sized and light and handy, for the windage of further 1 and second heat exchanger 2 of less First Heat Exchanger,
Increase the flow velocity of First Heat Exchanger 1 and 2 apoplexy of the second heat exchanger, the utility model will be arranged to be changed in First Heat Exchanger 1 and second
The number of rows of 2 inside copper pipe of hot device is reduced, and the copper pipe number of the First Heat Exchanger 1 of this programme and the second heat exchanger 2 is 3, relatively
It is 4 in the copper pipe number of finned heat exchanger in the prior art, the copper pipe number of the finned heat exchanger of this programme is reduced, from
And making the heat exchange efficiency higher of First Heat Exchanger 1 and the second heat exchanger 2, defrosting speed is faster；
There are two interfaces for the tool of First Heat Exchanger 1, and respectively mouth a mouthfuls and b mouthfuls, the second heat exchanger 2 has there are two interface, point
Wei not be a mouthfuls and b mouthfuls, a mouths of First Heat Exchanger 1 and the s mouths of the first four-way valve 55 connect, the b mouths and the first mould of First Heat Exchanger 1
Formula changeover module 3 connects, the s mouths connection of a mouths of the second heat exchanger 2 and the second four-way valve 6, the b mouths of the second heat exchanger 2 and the
Two modes changeover module 4 connects.
Further, it is a kind of parallel connection Cascade type heat pump system, including defrosting circulation loop, first heating circulation loop,
Second heating circulation loop, third heating circulation loop and the 4th heating circulation loop.
Defrosting mode：
Defrosting circulation loop is respectively provided with the first defrosting circulation branch road and the second defrosting circulation branch road in defrost mode, this
Scheme is respectively with circulation loop, the second defrosting circulation branch road and the heat exchanger group of the first defrosting circulation branch road and heat exchanger group
Circulation loop illustrate.
The defrosting circuit of first defrosting circulation branch road and heat exchanger group composition：As shown in Figure 1, the first compressor 7 compresses
The cold media gas of the high temperature and pressure generated afterwards passes through the D mouths of the first four-way valve 5 and E mouthfuls after the discharge of a mouths of the first compressor 7
The a mouths of First Heat Exchanger 1 are flow to, and are defrosted in First Heat Exchanger 1, the cold media gas First Heat Exchanger of high temperature and pressure
After discharging enough heats to the cold inside 1, become the refrigerant liquid of cryogenic high pressure, the cooling medium liquid of the cryogenic high pressure after the completion of defrosting
Body passes through the first check valve 32 and the first electric expansion valve 31 of first mode changeover module 3, after throttling, cryogenic high pressure
The decompression of refrigerant liquid become the refrigerant liquid of low-temp low-pressure, the refrigerant of the low-temp low-pressure in first mode changeover module 3
The refrigerant liquid of liquid and the low-temp low-pressure in second mode changeover module 4 flow to the b mouths and c of the first triple valve 9 respectively
Mouth is collaborated, and the refrigerant liquid of the low-temp low-pressure behind interflow flows out to the d of third heat exchanger 12 from a mouths of the first triple valve 9
In mouth, e mouthfuls and f mouthfuls, then refrigerant liquid in part is branched to from third triple valve 11 in the 4th heat exchanger 13, then refrigerant liquid
It is flow to from the 4th heat exchanger 13 and is evaporated the cold media gas for becoming low-temp low-pressure in the 6th heat exchanger 21, wherein third is changed
The evaporator of hot device 12, the 4th heat exchanger 13 and the 6th heat exchanger 21 as this defrosting circulation loop, third heat exchanger 12 and the
The main function of four heat exchangers 13 is to provide refrigerant liquid of the heat to low-temp low-pressure, to the refrigerant liquid for low-temp low-pressure
Evaporation in the 6th heat exchanger 21 provides heat, and refrigerant liquid is made to more easily reach its boiling point, the 6th heat exchanger in evaporation
21 are mainly evaporated for refrigerant liquid, are flow in the second triple valve 10 finally by the C mouths and S mouthfuls of the first four-way valve 5, and
And collaborated with the cold media gas of the low-temp low-pressure through pervaporation in second circulation circuit, the low-temp low-pressure behind interflow
Cold media gas some the gas returning port of the first compressor 7 is back to by the second port of the second triple valve 10.
The defrosting circuit of second defrosting circulation branch road and heat exchanger group composition：As shown in Figure 1, the second compressor 8 compresses
The cold media gas of the high temperature and pressure generated afterwards passes through the D mouths of the second four-way valve 6 and E mouthfuls after the discharge of a mouths of the second compressor 8
The a mouths of the second heat exchanger 2 are flow to, and are defrosted in the second heat exchanger 2, the cold media gas of high temperature and pressure is in the second heat exchange
After dischargeing enough heats to the cold inside device 2, become the refrigerant liquid of cryogenic high pressure, the cryogenic high pressure after the completion of defrosting it is cold
Matchmaker's liquid passes through the second check valve 42 and the second electric expansion valve 41 in second mode changeover module 4, after throttling, low temperature
The refrigerant liquid decompression of high pressure becomes the refrigerant liquid of low-temp low-pressure, the low-temp low-pressure from second mode changeover module 4 it is cold
The refrigerant liquid of matchmaker's liquid and the low-temp low-pressure from first mode changeover module 3 flow to the second end of the first triple valve 9 respectively
Mouth and third port are collaborated, and the refrigerant liquid of the low-temp low-pressure behind interflow flows out to third from a mouths of the first triple valve 9 and changes
In the d mouths of hot device 12, e mouthfuls and f mouthfuls, the refrigerant liquid of low-temp low-pressure flows out to the second threeway from the c mouths of third heat exchanger 12
In valve 10, then refrigerant liquid in part is branched to from the second triple valve 10 in the 5th heat exchanger 14, and then cold media gas is from the 5th
It is flow in heat exchanger 14 in the 7th heat exchanger 22 and is evaporated the cold media gas for becoming low-temp low-pressure, wherein third heat exchanger 12,
The evaporator of 5th heat exchanger 14 and the 7th heat exchanger 22 as this defrosting circulation loop, third heat exchanger 12 and the 5th exchange heat
The main function of device 14 is to provide refrigerant liquid of the heat to low-temp low-pressure, and refrigerant liquid is made to more easily reach its boiling in evaporation
Point provides energy with evaporation of the refrigerant liquid for low-temp low-pressure in the 7th heat exchanger 22, and the 7th heat exchanger 22 mainly supplies
Refrigerant liquid is evaporated, and is flow in the second triple valve 10 finally by the C mouths and S mouthfuls of the second four-way valve 6, and with from
The cold media gas of the low-temp low-pressure through pervaporation is collaborated in first circulation circuit, the cold media gas of the low-temp low-pressure behind interflow
Some is back to the gas returning port of the second compressor 8 by the second port of the second triple valve 10.
Heating mode：
First heating circulation loop：As shown in Figure 1, the cold media gas of 7 compressed high temperature and pressure of the first compressor is from
After a mouths discharge of one compressor 7, it is flow in the 6th heat exchanger 21 by the d mouths and c mouthfuls of the first four-way valve 5, then again from the
It is flow in the 4th heat exchanger 13 in six heat exchangers 21, then cold media gas flow to third heat exchanger 12 from the 4th heat exchanger 13
The middle refrigerant liquid for carrying out condensation and becoming cryogenic high pressure, wherein the 6th heat exchanger 21, the 4th heat exchanger 13 and third heat exchanger 12
As the condenser of the first heating circulation loop, the main function of the 6th heat exchanger 21 and the 4th heat exchanger 13 is to absorb high temperature height
The heat of the cold media gas of pressure, to for liquefaction of the cold media gas in third heat exchanger 12 of high temperature and pressure be more easy into
Row, third heat exchanger 12 mainly liquefy for cold media gas, and the refrigerant liquid of cryogenic high pressure passes through the first triple valve 9, so
The refrigerant liquid of part cryogenic high pressure is flow to from the second port of the first triple valve 9 in the first heating power expansion valve 33 afterwards, low temperature
The refrigerant liquid of high pressure becomes the refrigerant liquid of low-temp low-pressure after the throttling of the first heating power expansion valve 33, then from the first heat exchange
The b mouths of device 1 enter the cold media gas that low-temp low-pressure is evaporated into inside First Heat Exchanger 1, finally by the first four-way valve 5
E mouthfuls and S mouthfuls, the three or three is flow to together with the cold media gas for the low-temp low-pressure that the second heat exchanger 2 flows out under heating mode
The cold media gas of a mouths of port valve 11, the low-temp low-pressure behind interflow branches to the first compressor 7 from the b oral areas of third triple valve 11
Gas returning port in.
Second heating circulation loop：As shown in Figure 1, the cold media gas of 8 compressed high temperature and pressure of the second compressor is from
After a mouths discharge of two compressors 8, it is flow in the 7th heat exchanger 22 by the d mouths and c mouthfuls of the second four-way valve 6, then again from the
It is flow in the 5th heat exchanger 14 in seven heat exchangers 22, then cold media gas flow to third heat exchanger 12 from the 5th heat exchanger 14
The middle refrigerant liquid for carrying out condensation and becoming cryogenic high pressure, wherein the 7th heat exchanger 22, the 5th heat exchanger 14 and third heat exchanger 12
As the condenser of the second heating circulation loop, the main function of the 7th heat exchanger 22 and the 5th heat exchanger 14 is to absorb high temperature height
The heat of the cold media gas of pressure is carried out so that liquefaction of the cold media gas for high temperature and pressure in third heat exchanger 12 is more easy,
Third heat exchanger 12 mainly liquefies for cold media gas, and the refrigerant liquid of cryogenic high pressure passes through the first triple valve 9, then will
The refrigerant liquid of part cryogenic high pressure is flow to from the c mouths of the first triple valve 9 in the second heating power expansion valve 43, cryogenic high pressure it is cold
Matchmaker's liquid becomes the refrigerant liquid of low-temp low-pressure after the throttling of the second heating power expansion valve 43, then from the b of the second heat exchanger 2
Mouth enters the cold media gas that low-temp low-pressure is evaporated into inside the second heat exchanger 2, finally by the E mouths and S of the second four-way valve 6
Mouthful, under heating mode third triple valve 11 is flow to together with the cold media gas for the low-temp low-pressure that the second heat exchanger 2 flows out
A mouths, the cold media gas of the low-temp low-pressure behind interflow branches to the return-air of the second compressor 8 from the c oral areas of third triple valve 11
In mouthful.
Third heats circulation loop：As shown in Figure 1, the cold media gas of 15 compressed high temperature and pressure of third compressor is from
After a mouths discharge of three compressors 15, it flow in the 8th heat exchanger 23, then flow to the tenth heat exchanger 19 and wherein carry out condensation change
At the refrigerant liquid of cryogenic high pressure, wherein the 8th heat exchanger 23 heats the cold of circulation loop with the tenth heat exchanger 19 as third
Condenser, the main function of the 8th heat exchanger 23 are the heats for the cold media gas for absorbing high temperature and pressure, the tenth heat exchanger 19 it is main
Effect is liquefied for cold media gas, and the refrigerant liquid of cryogenic high pressure becomes low after 17 reducing pressure by regulating flow of first throttling device
The refrigerant liquid of warm low pressure, then the refrigerant liquid of low-temp low-pressure flow to a mouths of the 4th heat exchanger 13, and enters the 4th heat exchanger
It is evaporated in 13, the refrigerant liquid of low-temp low-pressure becomes the cold media gas of low-temp low-pressure, the cold media gas of last low-temp low-pressure
It is flow in the gas returning port of third compressor 15 from the d mouths of the 4th heat exchanger 13.
4th heating circulation loop：As shown in Figure 1, the cold media gas of 16 compressed high temperature and pressure of the 4th compressor is from
After a mouths discharge of four compressors 16, it flow in the 9th heat exchanger 24, then flow to the 11st heat exchanger 20 and wherein condensed
Become the refrigerant liquid of cryogenic high pressure, wherein the 9th heat exchanger 24 and the 11st heat exchanger 20 are as the 4th heating circulation loop
Condenser, the main function of the 9th heat exchanger 24 is the heat for the cold media gas for absorbing high temperature and pressure, the 11st heat exchanger 20
Main function be to liquefy for cold media gas, the refrigerant liquid of cryogenic high pressure is after 18 reducing pressure by regulating flow of second throttling device
Become the refrigerant liquid of low-temp low-pressure, then the refrigerant liquid of low-temp low-pressure flow to a mouths of the 5th heat exchanger 14, and enters the 5th
It is evaporated in heat exchanger 14, the refrigerant liquid of low-temp low-pressure becomes the cold media gas of low-temp low-pressure, last low-temp low-pressure
Cold media gas is flow to from the d mouths of the 5th heat exchanger 14 in the gas returning port of the 4th compressor 16.
The above is only the preferred embodiment of the utility model, it is noted that for the common skill of the art
For art personnel, without deviating from the technical principle of the utility model, several improvement and replacement can also be made, these change
The scope of protection of the utility model is also should be regarded as into replacement.
Claims (10)
1. a kind of parallel connection Cascade type heat pump system, which is characterized in that including a plurality of defrosting/heating branch, a plurality of defrosting/system
It is sequentially connected in series to form defrosting/system with first direction control valve, heat exchanger assembly, second direction control valve after hot branch circuit parallel connection
Soft circulation circuit；
The defrosting/heating branch includes the compressor being sequentially connected in series, heat exchanger and pattern switching component.
2. parallel connection Cascade type heat pump system as described in claim 1, which is characterized in that the defrosting/heating branch is set as two
Item is followed successively by the first defrosting/heating branch and the second defrosting/heating branch；
First defrosting/heating branch includes that the first compressor, First Heat Exchanger and the first mode being sequentially connected in series are cut
Change component；
Second defrosting/heating branch includes that the second compressor, the second heat exchanger and second mode being sequentially connected in series are cut
Change component.
3. parallel connection Cascade type heat pump system as claimed in claim 2, which is characterized in that the first direction control valve is first
Triple valve, first triple valve are equipped with first port, second port and the third port for being located at described second port the same side,
The first port of first triple valve connects the heat exchanger group, the second port of first triple valve and described first
Pattern switching component connects, and the third port of first triple valve is connect with the second mode changeover module.
4. parallel connection Cascade type heat pump system as claimed in claim 2, which is characterized in that the second direction control valve is second
Triple valve, second triple valve are equipped with first port, second port and the third port for being located at described second port the same side,
The first port of second triple valve is connect with the heat exchanger group, the second port of second triple valve and described the
The gas returning port of one compressor connects, and the third port of second triple valve is connect with the gas returning port of second compressor.
5. parallel connection Cascade type heat pump system as claimed in claim 2, which is characterized in that each the pattern switching component includes
Two expansion valves being connected in parallel with each other, the heat pump switch different described swollen in the case where carrying out heating mode or defrosting mode
Swollen valve.
6. parallel connection Cascade type heat pump system as claimed in claim 5, which is characterized in that the first mode changeover module includes
First check valve, the first electric expansion valve and the first heating power expansion valve, first check valve and first electric expansion valve
It is connected in parallel with first heating power expansion valve after being connected in series with；
The second mode changeover module includes the second check valve, the second electric expansion valve and the second heating power expansion valve, and described the
Two check valves are connected in parallel after being connected in series with second electric expansion valve with second heating power expansion valve.
7. parallel connection Cascade type heat pump system as claimed in claim 6, which is characterized in that in defrosting mode, refrigerant leads to successively
Cross first compressor, First Heat Exchanger, the first check valve, the first electric expansion valve, the first triple valve and heat exchanger group
Connection forms the first defrosting circulation loop；
In heating mode, refrigerant pass sequentially through the first compressor, heat exchanger group, the first triple valve, the first heating power expansion valve,
First Heat Exchanger and the first compressor connect to form the first heating circulation loop；
In defrosting mode, refrigerant pass sequentially through the second compressor, the second heat exchanger, the second check valve, the second electric expansion valve,
First triple valve connects to form the second defrosting circulation loop with heat exchanger group；
In heating mode, refrigerant pass sequentially through the second compressor, heat exchanger group, the first triple valve, the second heating power expansion valve,
Second heat exchanger and the second compressor connect to form the second heating circulation loop.
8. parallel connection Cascade type heat pump system as claimed in claim 3, which is characterized in that in the defrosting circulation loop, institute
It includes third heat exchanger, the 4th heat exchanger, the 5th heat exchanger, the 6th heat exchanger and the 7th heat exchanger to state heat exchanger group, described
Third heat exchanger is connect with the first direction control valve, and the third heat exchanger is exchanged heat by third triple valve and the described 4th
Device and the connection of the 5th heat exchanger, the 4th heat exchanger are connect with six heat exchanger, the 5th heat exchanger and the described 7th
Heat exchanger connects, and the 6th heat exchanger and the 7th heat exchanger are connected by the second direction control valve.
9. parallel connection Cascade type heat pump system as claimed in claim 8, which is characterized in that the third heat exchanger have a, b, c,
The a mouths of six ports e and f d, the third heat exchanger are connect with the air injection enthalpy-increasing mouth of second compressor, and the third is changed
The b mouths of hot device are connect with the air injection enthalpy-increasing mouth of first compressor, c mouths and the third triple valve of the third heat exchanger
First port connection, d, e and f mouth of the third heat exchanger connect with the first port of first triple valve.
10. parallel connection Cascade type heat pump system as claimed in claim 8, which is characterized in that further include the first four-way valve and second
The S mouths of four-way valve, first four-way valve are connect with the gas returning port of first compressor, the E mouths of first four-way valve with
The First Heat Exchanger connection, the C mouths of first four-way valve are connect with the 6th heat exchanger, the D of first four-way valve
Mouth is connect with the exhaust outlet of first compressor；
The S mouths of second four-way valve are connect with the gas returning port of second compressor, the E mouths of second four-way valve with it is described
Second heat exchanger connects, and C mouths of second four-way valve connect with the 7th heat exchanger, the D mouths of second four-way valve and
The exhaust outlet of second compressor connects.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201721921252.3U CN207763308U (en) | 2017-12-28 | 2017-12-28 | A kind of parallel connection Cascade type heat pump system |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201721921252.3U CN207763308U (en) | 2017-12-28 | 2017-12-28 | A kind of parallel connection Cascade type heat pump system |
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| CN207763308U true CN207763308U (en) | 2018-08-24 |
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Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN108036557A (en) * | 2017-12-28 | 2018-05-15 | 广东芬尼克兹节能设备有限公司 | A kind of parallel connection Cascade type heat pump system |
| CN110701814A (en) * | 2019-10-12 | 2020-01-17 | 珠海格力电器股份有限公司 | Refrigeration dual system with stable operation during defrosting |
-
2017
- 2017-12-28 CN CN201721921252.3U patent/CN207763308U/en active Active
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN108036557A (en) * | 2017-12-28 | 2018-05-15 | 广东芬尼克兹节能设备有限公司 | A kind of parallel connection Cascade type heat pump system |
| CN108036557B (en) * | 2017-12-28 | 2023-11-14 | 广东芬尼克兹节能设备有限公司 | Parallel cascade heat pump system |
| CN110701814A (en) * | 2019-10-12 | 2020-01-17 | 珠海格力电器股份有限公司 | Refrigeration dual system with stable operation during defrosting |
| CN110701814B (en) * | 2019-10-12 | 2020-11-24 | 珠海格力电器股份有限公司 | Refrigeration dual system with stable operation during defrosting |
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