CN211876422U - Improved low-temperature air source cold and warm heat pump - Google Patents
Improved low-temperature air source cold and warm heat pump Download PDFInfo
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- CN211876422U CN211876422U CN201922375347.5U CN201922375347U CN211876422U CN 211876422 U CN211876422 U CN 211876422U CN 201922375347 U CN201922375347 U CN 201922375347U CN 211876422 U CN211876422 U CN 211876422U
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Abstract
The utility model discloses an improved generation low temperature air source changes in temperature heat pump, it includes: the system comprises a compressor, a four-way valve, a condenser, a one-way valve group, an economizer, a liquid storage tank, a heat exchanger and a gas-liquid separator, wherein the heat exchanger is connected with the four-way valve, the gas-liquid separator is connected with the compressor, and the liquid storage tank is communicated with the one-way valve group through a main path throttling device and an auxiliary path throttling device which are connected in parallel; the condenser is provided with a refrigerant channel and a water flow channel; the check valve set is arranged between a refrigerant channel of the condenser and the heat exchanger and consists of two groups of check valve sets which are connected in parallel. The utility model discloses simple structure, the low temperature operation advantage, it adopts the check valve group to replace the check valve in a plurality of different pipelines in original product, utilizes the flow direction of check valve group self-control refrigerant, and its simple structure moves stably to be convenient for maintain and change.
Description
The technical field is as follows:
the utility model relates to a heat pump product technical field refers in particular to an improved generation low temperature air source changes in temperature heat pump.
Background art:
the decrease of the outdoor temperature in winter can reduce the heat absorption capacity of the refrigerant in the evaporator of the heat pump system to the outdoor air, and simultaneously, the evaporation pressure is reduced, the air suction capacity is reduced, and the heating capacity and the operation power attenuation are reduced.
Furthermore, the efficiency of the compressor in the heat pump system is reduced due to the reduction of the outdoor temperature in winter, and as mentioned above, when the outdoor temperature in winter is reduced, the evaporation temperature T0 and the evaporation pressure P0 are also reduced, while the condensation pressure PK is not greatly changed due to the restriction of the medium (indoor air and water), which inevitably causes the compression ratio PK/P0 to increase, and the increase of the compression ratio causes the compressor to increase irreversibly in the working process (the exhaust temperature is increased, and the compressor is damaged due to long-term high exhaust temperature operation), and the efficiency is reduced, so that the reduction of the working efficiency of the compressor at low outdoor temperature is also one of the reasons for the insufficient output of the air-cooled heat pump.
Aiming at the problem of insufficient output of the heat pump in winter, the scheme at present is mainly to add an economizer, further improve the supercooling degree of a refrigerant through the heat exchange of the economizer and increase the air input of a compressor, thereby overcoming the problem of low-temperature operation efficiency reduction of the compressor. However, the existing heat pump product pipeline is complex in design and is difficult to ensure stable operation. In addition, the existing heat pump throttling device mostly adopts a thermal expansion valve to realize automatic control, but the adjustment range of the thermal expansion valve is limited. In an extremely cold environment, a smaller thermostatic expansion valve is selected due to low flow, but when the ambient temperature rises, the smaller thermostatic expansion valve cannot meet the working requirement and must be replaced, which undoubtedly increases the maintenance cost. The present inventors have made no matter what improvement, and have proposed the following technical solutions.
The utility model has the following contents:
the utility model discloses the problem that the claim was solved just lies in overcoming the not enough of prior art, provides an improved generation low temperature air source changes in temperature heat pump.
In order to solve the technical problem, the utility model discloses a following technical scheme: improved generation low temperature air source changes in temperature heat pump, this heat pump includes: the compressor, a four-way valve, a condenser, a one-way valve group, an economizer, a liquid storage tank, a heat exchanger and a gas-liquid separator which are sequentially connected with the compressor, wherein the heat exchanger is connected with the four-way valve, the gas-liquid separator is connected with the compressor, and the liquid storage tank is communicated with the one-way valve group through a main path throttling device and an auxiliary path throttling device which are connected in parallel; the condenser is provided with a refrigerant channel and a water flow channel; the check valve group is arranged between a refrigerant channel of the condenser and the heat exchanger, and the check valve group consists of two groups of check valve groups which are connected in parallel, wherein one group of check valve groups comprises: a first check valve and a second check valve, another set of check valve sets comprising: a third check valve and a fourth check valve; the economizer is connected between the first check valve and the second check valve; the main path throttling device is connected between a third check valve and a fourth check valve in the check valve group.
Further, in the above technical solution, the main throttle device adopts a thermostatic expansion valve, and the auxiliary throttle device adopts a capillary tube and an electromagnetic valve connected in series.
Furthermore, in the above technical solution, one path of the economizer communicates with the check valve set and the liquid storage tank, and the other path of the economizer communicates with the liquid storage tank and the compressor through an electronic expansion valve.
Further, in the above technical solution, the first check valve and the second check valve have opposite conduction directions; the third one-way valve and the fourth one-way valve are opposite in conducting direction.
Further, in the above technical solution, the outlet of the liquid storage tank is provided with a drying filter.
Further, in the above technical solution, a low pressure gauge and a low pressure protector are disposed on a passage between the compressor and the gas-liquid separator.
Further, in the above technical solution, a high pressure gauge and a high pressure protector are disposed on a channel between the compressor and the four-way valve.
Further, in the above technical scheme, a liquid storage tank needle valve is arranged at an inlet of the liquid storage tank.
Further, in the above technical solution, a separator needle valve is disposed at an inlet of the gas-liquid separator.
After the technical scheme is adopted, compared with the prior art, the utility model has following beneficial effect:
1. the structure is simple, the check valve group is adopted to replace check valves in a plurality of different pipelines in the original product, the flow direction of the refrigerant is automatically controlled by the check valve group, and the refrigerant circulating system is simple in structure, stable in operation and convenient to maintain and replace.
2. Low temperature operation, the utility model discloses can work under extremely cold environment, it increases the super-cooled rate of refrigerant through the economizer, further improves the air input of compressor, improves the work efficiency of compressor. Simultaneously, adopt main road expansion valve and the parallelly connected refrigerant throttle flow of adjusting of auxiliary road expansion valve to the order the utility model discloses also can normal operating after ambient temperature risees.
Description of the drawings:
fig. 1 is a schematic structural diagram of the present invention.
The specific implementation mode is as follows:
the present invention will be further described with reference to the following specific embodiments and accompanying drawings.
As shown in fig. 1, the improved low-temperature air source cooling and heating heat pump comprises a compressor 1, a four-way valve 2, a condenser 3, a one-way valve bank 4, an economizer 5, a liquid storage tank 6, a heat exchanger 7, a gas-liquid separator 8, a main path throttling device and an auxiliary path throttling device.
The inlet of the compressor 1 is communicated with the gas-liquid separator 8, and a low-pressure meter 81 and a low-pressure protector 82 are arranged on a channel between the inlet of the compressor 1 and the gas-liquid separator 8. An outlet of the compressor 1 is connected to the four-way valve 2, and a high pressure gauge 11 and a high pressure protector 12 are provided on a passage between the compressor 1 and the four-way valve 2. And different channels are switched to be communicated by controlling the four-way valve 2.
The condenser 3 adopts a coaxial double-pipe heat exchanger and is provided with a refrigerant channel and a water flow channel, wherein one end of the refrigerant channel is communicated with the four-way valve 2, and the other end of the refrigerant channel is communicated with the check valve group 4.
Check valve group 4 set up between the refrigerant passageway of condenser 3 and heat exchanger 7, it comprises two sets of check valve groups that connect in parallel, one of them group check valve group includes: a first check valve 41 and a second check valve 42, the other set of check valve groups comprising: a third check valve 43 and a fourth check valve 44. The first check valve 41 and the second check valve 42 are opposite in conducting direction; the third check valve 43 and the fourth check valve 44 are communicated in opposite directions. Referring to fig. 1, specifically, the first check valve 41 may be turned on from top to bottom; the second one-way valve 42 can be communicated from bottom to top; the third check valve 43 can be conducted from bottom to top; the fourth check valve 44 may be open from top to bottom.
The economizer 5 adopts a plate heat exchanger, one channel of the economizer 5 is communicated with the check valve group 4 and the liquid storage tank 6, specifically, one channel of the economizer 5 is connected between a first check valve 41 and a second check valve 42 in the check valve group 4, and the other end of the channel is communicated with the liquid storage tank 6. One end of the other channel of the economizer 5 is communicated with the liquid storage tank 6 after passing through an electronic expansion valve 94 and the drying filter 61, the other end of the other channel is communicated with the compressor 1, and a pressure sensor 13 is arranged on the channel between the economizer 5 and the compressor 1. The inlet of the liquid storage tank 6 is provided with a liquid storage tank needle valve 62.
A main road throttling device and an auxiliary road throttling device which are connected in parallel are arranged between the drying filter 61 and the check valve group 4 and are communicated with the check valve group 4; the parallel main and auxiliary throttle devices are connected between the third and fourth check valves 43, 44 in the check valve group 4. The main throttle device adopts a thermostatic expansion valve 91, and the auxiliary throttle device adopts a capillary tube 92 and an electromagnetic valve 93 which are connected in series.
The heat exchanger 7 adopts a finned heat exchanger, one end of the finned heat exchanger is connected to the check valve group 4, and the other end of the finned heat exchanger is connected to the four-way valve 2.
The gas-liquid separator 8 is connected between the four-way valve 2 and the compressor 1, wherein a separator needle valve 83 is provided on a pipe between the four-way valve 2 and the gas-liquid separator 8, that is, the separator needle valve 83 is provided at an inlet of the gas-liquid separator 8.
The accumulator needle valve 62 and the separator needle valve 83 described above are adapted to replenish the refrigerant.
The following describes the working process of the present invention in detail. The utility model discloses two kinds of mode have: the heating mode and the cooling mode are specifically described below.
Heating mode:
the compressor 1 compresses a refrigerant to form a high-temperature and high-pressure refrigerant, and the high-temperature and high-pressure refrigerant passes through the high-pressure gauge 11 and the high-pressure protector 12 and then enters the four-way valve 2. At this time, the four-way valve 2 is controlled to communicate the refrigerant passages of the compressor 1 and the condenser 3. As shown in fig. 1, the high-temperature and high-pressure refrigerant flows through the refrigerant passage of the condenser 3 from the top down. And the cold water to be heated passes through the water flow channel of the condenser from bottom to top. The refrigerant and the water flow realize heat exchange in the condenser, the refrigerant with the reduced temperature enters the check valve group 4, and the water flow with the increased temperature is discharged for the common user.
After the low-temperature and high-pressure refrigerant flowing out of the condenser 3 enters the check valve group 4, the third check valve 43 cannot be opened, and therefore the refrigerant can enter only from the first check valve 41. At this time, the second check valve 42 cannot be opened, and therefore the refrigerant 5 entering the economizer 5 flows into the economizer. Enters a liquid storage tank 6 after passing through an economizer 5. After passing through the filter drier 61, the refrigerant flows to the thermal expansion valve 91, and the bypass throttle device is not operated. The pressure is reduced after throttling by the thermostatic expansion valve 91. The refrigerant of low pressure again enters between the third check valve 43 and the fourth check valve 44 in the single-phase valve block 4. Since the high-pressure refrigerant outside the third check valve 43 resists being conducted, the low-pressure refrigerant can only push the fourth check valve 44 open to the heat exchanger 7.
The heat exchanger 7 is a fin-type heat exchanger, and the low-pressure refrigerant evaporates by absorbing heat in air in the heat exchanger 7. The evaporated refrigerant gas will flow to the four-way valve 2 again. The four-way valve 2 is used for realizing the communication between the heat exchanger 7 and the gas-liquid separator 8, and the refrigerant enters the gas-liquid separator 8.
Finally, the refrigerant passes through the low pressure gauge 81 and the low pressure protector 82 in sequence by the gas-liquid separator 8 and then reenters the compressor 1, and the gas-state refrigerator is compressed into a high-temperature high-pressure liquid-state refrigerant by the compressor 1, thereby completing a cycle. In the above process, cold water continuously flows into the condenser 3, and the high-temperature and high-pressure refrigerant flowing through the condenser 3 exchanges heat with the cold water, so that the condenser 3 can supply high-temperature hot water.
In addition, in a low-temperature environment, since the ambient temperature is too low, the amount of refrigerant evaporated decreases, which causes a decrease in the amount of suction of the compressor, and a decrease in the operating efficiency. The low temperature environment is decreased by opening the electronic expansion valve 94 to increase the compressor suction and increase the degree of subcooling of the refrigerant in order to increase the compressor suction. Specifically, the refrigerant passes through the dry filter 61, flows to the thermal expansion valve 91, is throttled by the thermal expansion valve 91, and flows to the heat exchanger 7 through the single-phase valve group 4. Meanwhile, a part of the refrigerant is introduced into the economizer 5 by controlling the electronic expansion valve 94, throttled by the electronic expansion valve 94, and evaporated. The refrigerant absorbs heat in the evaporation process, so that latent heat in the refrigerant at the high-pressure end can be absorbed, and the supercooling degree of the refrigerant is further improved. And the refrigerant at the evaporation end directly enters the compressor 1 after absorbing heat, so that the suction capacity of the compressor 1 is improved, and the power of the compressor is ensured.
The utility model discloses still dispose the accessory road throttling arrangement, its capillary 92 and the solenoid valve 93 that adopts the series connection. This is because the range of the adjustment is effective as the thermostatic expansion valve 91 to which the main throttle is adjusted. Work as the utility model discloses the heat pump works under extremely cold condition, and thermal expansion valve 91 just can not dispose too big, if too big just can't play the throttle step-down effect to the refrigerant. Therefore, in an extremely cold environment, only a smaller thermostatic expansion valve can be used as the thermostatic expansion valve 91. When the ambient temperature rises, the smaller thermostatic expansion valve 91 cannot meet the working requirement, and the auxiliary throttle adjusting device needs to be opened at the moment. At the moment, the main road throttling device and the auxiliary road throttling device which are connected in parallel participate in throttling at the same time so as to meet the working requirement. The electromagnetic valve 93 in the auxiliary road throttle device is not opened in an extremely cold environment and is in a closed state. When the ambient temperature rises (generally, when the ambient temperature is higher than 15 ℃), the electromagnetic valve 93 is opened, and at this time, the capillary tube 92 works to participate in throttling the refrigerant, so that the working requirement is met. On the same reason, when the utility model enters the refrigeration mode to carry out refrigeration operation, the auxiliary relay device is also opened to participate in throttling.
A refrigeration mode:
the compressor 1 compresses a refrigerant to form a high-temperature and high-pressure refrigerant, and the high-temperature and high-pressure refrigerant passes through the high-pressure gauge 11 and the high-pressure protector 12 and then enters the four-way valve 2. At this time, the four-way valve 2 is controlled to communicate the compressor 1 with the heat exchanger 7. As shown in fig. 1, the high-temperature and high-pressure refrigerant passes through the four-way valve 2, enters the heat exchanger 7, releases heat to air through the heat exchanger 7, and enters the check valve bank 4.
After the low-temperature and high-pressure refrigerant flowing out of the heat exchanger 7 enters the check valve group 4, the fourth check valve 44 cannot be opened, and therefore the refrigerant can enter only from the second check valve 42. At this time, the first check valve 41 cannot be opened, and therefore the refrigerant 5 that has entered flows into the economizer 5. Enters a liquid storage tank 6 after passing through an economizer 5. After passing through the dry filter 61, the air flows to the main path throttle device and the sub path throttle device, and the pressure is reduced by throttling the air by the thermostatic expansion valve 91 and the capillary tube 92. The refrigerant of low pressure again enters between the third check valve 43 and the fourth check valve 44 in the single-phase valve block 4. Since the high pressure refrigerant outside the fourth check valve 44 resists being conducted, the low pressure refrigerant can only push the third check valve 43 open to the condenser 3.
After passing through the check valve group 4, the refrigerant enters the condenser 3 from bottom to top and starts to absorb heat to evaporate, and meanwhile, the heat of the water flow flowing through the water flow channel in the condenser 3 is continuously absorbed, the temperature is reduced, and finally the refrigerant flows out after being changed into cold water.
The refrigerant with the increased temperature flows out of the condenser 3 and then enters the four-way valve 2, the condenser 3 is communicated with the gas-liquid separator 8 through the four-way valve 2, and the refrigerant enters the gas-liquid separator 8.
Finally, the refrigerant passes through the low pressure gauge 81 and the low pressure protector 82 in sequence by the gas-liquid separator 8 and then reenters the compressor 1, and the gas-state refrigerator is compressed into a high-temperature high-pressure liquid-state refrigerant by the compressor 1, thereby completing a cycle. In the above process, hot water continuously flows into the condenser 3, and the low-temperature and low-pressure refrigerant flowing through the condenser 3 exchanges heat with the hot water, so that the condenser 3 can supply low-temperature cold water.
Of course, the above description is only an exemplary embodiment of the present invention, and not intended to limit the scope of the present invention, and all equivalent changes and modifications made by the constructions, features, and principles of the present invention in accordance with the claims of the present invention are intended to be included in the scope of the present invention.
Claims (9)
1. The utility model provides an improved generation low temperature air source changes in temperature heat pump which characterized in that: the heat pump includes: the air conditioner comprises a compressor (1), a four-way valve (2), a condenser (3), a one-way valve bank (4), an economizer (5), a liquid storage tank (6), a heat exchanger (7) and a gas-liquid separator (8), wherein the four-way valve (2), the condenser (3), the heat exchanger (7) and the gas-liquid separator (8) are sequentially connected with the compressor (1), the gas-liquid separator (8) is connected with the compressor (1), and the liquid storage tank (6) is communicated with the one-way valve bank (4) through a main path throttling device and an auxiliary path throttling device which are;
the condenser (3) is provided with a refrigerant channel and a water flow channel;
check valve group (4) set up between refrigerant passageway and heat exchanger (7) of condenser (3), this check valve group (4) comprises two sets of check valve group that connect in parallel, wherein a set of check valve group includes: a first check valve (41) and a second check valve (42), the other set of check valve sets comprising: a third check valve (43) and a fourth check valve (44); the economizer (5) is connected between the first check valve (41) and the second check valve (42); the main path throttling device is connected between a third check valve (43) and a fourth check valve (44) in the check valve group (4).
2. The improved low-temperature air source cold-warm heat pump as claimed in claim 1, characterized in that: the main throttle device adopts a thermostatic expansion valve (91), and the auxiliary throttle device adopts a capillary tube (92) and an electromagnetic valve (93) which are connected in series.
3. The improved low-temperature air source cold-warm heat pump as claimed in claim 2, characterized in that: one channel of the economizer (5) is communicated with the check valve group (4) and the liquid storage tank (6), and the other channel is communicated with the liquid storage tank (6) and the compressor (1) through an electronic expansion valve (94).
4. The improved low-temperature air source cold-warm heat pump as claimed in claim 2, characterized in that: the first check valve (41) and the second check valve (42) are opposite in conducting direction; the third check valve (43) and the fourth check valve (44) are opposite in conducting direction.
5. The improved low-temperature air source cold-warm heat pump as claimed in claim 2, characterized in that: the outlet of the liquid storage tank (6) is provided with a drying filter (61).
6. The improved low-temperature air source cold-warm heat pump as claimed in claim 2, characterized in that: a low-pressure meter (81) and a low-pressure protector (82) are arranged on a channel between the compressor (1) and the gas-liquid separator (8).
7. The improved low-temperature air source cold-warm heat pump as claimed in claim 2, characterized in that: and a high-pressure gauge (11) and a high-pressure protector (12) are arranged on a channel between the compressor (1) and the four-way valve (2).
8. The improved low-temperature air source cold-warm heat pump as claimed in claim 2, characterized in that: the inlet of the liquid storage tank (6) is provided with a liquid storage tank needle valve (62).
9. The improved low-temperature air source cold-warm heat pump as claimed in claim 2, characterized in that: and a separator needle valve (83) is arranged at the inlet of the gas-liquid separator (8).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201922375347.5U CN211876422U (en) | 2019-12-25 | 2019-12-25 | Improved low-temperature air source cold and warm heat pump |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201922375347.5U CN211876422U (en) | 2019-12-25 | 2019-12-25 | Improved low-temperature air source cold and warm heat pump |
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| Publication Number | Publication Date |
|---|---|
| CN211876422U true CN211876422U (en) | 2020-11-06 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201922375347.5U Active CN211876422U (en) | 2019-12-25 | 2019-12-25 | Improved low-temperature air source cold and warm heat pump |
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| Country | Link |
|---|---|
| CN (1) | CN211876422U (en) |
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2019
- 2019-12-25 CN CN201922375347.5U patent/CN211876422U/en active Active
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