CN213178585U - Throttling device of refrigerant circulation system, refrigerant circulation system and air conditioner - Google Patents
Throttling device of refrigerant circulation system, refrigerant circulation system and air conditioner Download PDFInfo
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- CN213178585U CN213178585U CN202022283756.5U CN202022283756U CN213178585U CN 213178585 U CN213178585 U CN 213178585U CN 202022283756 U CN202022283756 U CN 202022283756U CN 213178585 U CN213178585 U CN 213178585U
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- 239000003507 refrigerant Substances 0.000 title claims abstract description 119
- 238000011144 upstream manufacturing Methods 0.000 claims abstract description 8
- 238000004891 communication Methods 0.000 claims description 5
- 230000006698 induction Effects 0.000 abstract description 2
- 239000007788 liquid Substances 0.000 description 8
- 238000005452 bending Methods 0.000 description 5
- 230000009286 beneficial effect Effects 0.000 description 3
- 238000010586 diagram Methods 0.000 description 3
- 238000004378 air conditioning Methods 0.000 description 2
- 230000005494 condensation Effects 0.000 description 2
- 238000009833 condensation Methods 0.000 description 2
- 238000001704 evaporation Methods 0.000 description 2
- 230000008020 evaporation Effects 0.000 description 2
- 230000008859 change Effects 0.000 description 1
- 238000001816 cooling Methods 0.000 description 1
- 230000029087 digestion Effects 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 230000009467 reduction Effects 0.000 description 1
- 238000005057 refrigeration Methods 0.000 description 1
- 238000004088 simulation Methods 0.000 description 1
- 238000004804 winding Methods 0.000 description 1
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Abstract
The utility model relates to a throttling arrangement, refrigerant circulation system and air conditioner of refrigerant circulation system, the throttling arrangement of refrigerant circulation system includes: a refrigerant inlet (8); a refrigerant outlet (9); the throttling component (5) is positioned between the refrigerant inlet (8) and the refrigerant outlet (9) along the refrigerant flowing direction; and the bypass pressure relief pipeline (6) is positioned between the refrigerant inlet (8) and the refrigerant outlet (9) along the refrigerant flowing direction and is connected with the throttling component (5) in parallel, so that the upstream pressure and the downstream pressure of the throttling component (5) are balanced after the refrigerant circulating system is stopped and the throttling component (5) is closed. Use the technical scheme of the utility model, the pressure differential of gas vent and induction port is great when having improved the compressor restart leads to starting too big problem of moment of torsion moment in the twinkling of an eye.
Description
Technical Field
The utility model relates to a refrigeration plant field particularly, relates to a throttling arrangement, refrigerant circulation system and air conditioner of refrigerant circulation system.
Background
The refrigerant circulating system of the air conditioner comprises a compressor, a condenser, a throttling component and an evaporator. The inlet of the condenser is communicated with the exhaust port of the compressor, the inlet of the throttling component is communicated with the outlet of the condenser, the outlet of the throttling component is communicated with the inlet of the evaporator, and the outlet of the evaporator is communicated with the air suction port of the compressor. The high-temperature and high-pressure refrigerant compressed by the compressor is condensed in the condenser, the condensed refrigerant enters the evaporator after being throttled by the throttling component to be evaporated and absorb heat, and the evaporated refrigerant enters the compressor to be compressed again. The compressor is the power source of the whole system, the throttling component is used for realizing the function of throttling and reducing pressure, and the low-temperature and low-pressure working medium after throttling is changed into a high-pressure and high-temperature working medium after positive work is done by the compressor.
In the normal case: the air conditioning system follows the logic of three controls of starting, stopping and stopping, namely, the compressor can be started after the air conditioning system is started to operate for more than six minutes and stopped for more than three minutes.
When the air conditioner is shut down, the throttling component is quickly closed, so that the pressure difference between the high-pressure side (positioned at the upstream of the throttling component in the refrigerant flowing direction) and the low-pressure side (positioned at the downstream of the throttling component in the refrigerant flowing direction) of the system is larger, and the high-pressure difference and the low-pressure difference are still larger after three minutes; for the air conditioner adopting the single-phase rotor compressor, the compressor is started at the moment, the moment torque is overlarge due to the fact that the pressure difference between the front and the back of the compressor is large, the starting current is overlarge and exceeds the rated set current value of the compressor, and the overload protection of the compressor occurs.
SUMMERY OF THE UTILITY MODEL
The utility model aims at providing a refrigerant circulation system's throttling arrangement, refrigerant circulation system and air conditioner to improve the problem that refrigerant circulation system shuts down the upstream part of back throttling component and the pressure of low reaches part can not be balanced among the correlation technique.
According to the utility model discloses an aspect provides a refrigerant circulation system's throttling arrangement, refrigerant circulation system's throttling arrangement includes:
a refrigerant inlet;
a refrigerant outlet;
the throttling component is positioned between the refrigerant inlet and the refrigerant outlet along the refrigerant flowing direction; and
and the bypass pressure relief pipeline is positioned between the refrigerant inlet and the refrigerant outlet along the refrigerant flowing direction and is connected with the throttling component in parallel so as to balance the upstream and downstream pressures of the throttling component after the refrigerant circulating system is stopped and the throttling component is closed.
In some embodiments of the present invention, the,
the bypass pressure relief pipeline comprises a capillary tube; or
A control valve is arranged in the bypass pressure relief pipeline.
In some embodiments, the bypass pressure relief line includes a bend located at an end of the bypass pressure relief line adjacent the refrigerant inlet.
In some embodiments, the bypass pressure relief line further comprises a coiled tubing section in communication with the elbow section.
In some embodiments, the coiled tubing segment is coiled 1 to 3 times.
In some embodiments, the throttling device further comprises a connecting pipe section, a first end of the connecting pipe section is communicated with the bent pipe section, a second end of the connecting pipe section is communicated with the coiled pipe section, and the bent pipe section and the coiled pipe section are arranged at intervals in the circumferential direction of the connecting pipe section.
In some embodiments, the bent and coiled tube sections are spaced apart in the circumferential direction of the connecting tube section by an angle a, wherein angle a is 60 to 80 degrees.
In some embodiments of the present invention, the,
the connecting pipe section is connected with the outlet end of the bent pipe section and extends towards the coiled pipe section along the tangential direction of the bent pipe section;
the connecting tube section is connected to the inlet end of the coiled tube section and extends in a tangential direction of the coiled tube section toward the bend section.
According to the utility model discloses an on the other hand still provides a refrigerant circulation system, and refrigerant circulation system includes:
a compressor;
the condenser is communicated with an exhaust port of the compressor;
the evaporator comprises an inlet communicated with the condenser and an outlet communicated with an air suction port of the compressor; and
the throttling device is positioned between the condenser and the evaporator along the flowing direction of the refrigerant.
According to the utility model discloses an on the other hand still provides an air conditioner, and this air conditioner includes foretell refrigerant circulation system.
Use the technical scheme of the utility model, after refrigerant circulation system shut down, bypass pressure release pipeline can communicate the upper reaches pipeline of throttling component and the low reaches pipeline of throttling component for refrigerant circulation system shuts down the pressure balance of the upper reaches part of back throttling component and low reaches part, and the pressure difference of gas vent and induction port is great when having improved the compressor restart and is leaded to starting the too big problem of moment of torsion in the twinkling of an eye.
Other features of the present invention and advantages thereof will become apparent from the following detailed description of exemplary embodiments of the invention, which proceeds with reference to the accompanying drawings.
Drawings
In order to more clearly illustrate the technical solutions of the embodiments of the present invention or the related art, the drawings required to be used in the description of the embodiments or the related art will be briefly introduced below, it is obvious that the drawings in the following description are only some embodiments of the present invention, and for those skilled in the art, other drawings can be obtained according to these drawings without inventive labor.
Fig. 1 shows a schematic structural view of a condensation cycle system according to an embodiment of the present invention;
fig. 2 shows a schematic structural view of a throttling device of a condensation circulation system according to an embodiment of the present invention;
fig. 3 is a schematic structural view illustrating a bypass throttling pipeline of a throttling device of a refrigerant circulation system according to an embodiment of the present invention;
fig. 4 is a schematic side view of a bypass throttling pipeline of a throttling device of a refrigerant circulation system according to an embodiment of the present invention;
fig. 5 is a schematic structural diagram of a bypass throttle pipeline of a throttle device of a refrigerant circulation system according to an embodiment of the present invention.
Detailed Description
The technical solutions in the embodiments of the present invention will be described clearly and completely with reference to the accompanying drawings in the embodiments of the present invention, and it is obvious that the described embodiments are only some embodiments of the present invention, not all embodiments. The following description of at least one exemplary embodiment is merely illustrative in nature and is in no way intended to limit the invention, its application, or uses. Based on the embodiments in the present invention, all other embodiments obtained by a person skilled in the art without creative efforts belong to the protection scope of the present invention.
Fig. 1 is a schematic structural diagram of a refrigerant circulation system according to the present embodiment. As shown in fig. 1, the refrigerant circulation system includes a compressor 1, a condenser 2, a throttle device, and an evaporator 7, which are sequentially arranged in a refrigerant flow direction. The refrigerant circulation system further includes a first fan 3 for causing air to flow toward the condenser 2 to exchange heat therewith and a second fan for causing air to flow toward the evaporator 7 to exchange heat therewith.
The refrigerant compressed by the compressor 1 flows into the condenser 2, the refrigerant condensed in the condenser 2 flows into the evaporator 7 after being throttled by the throttling device, and the refrigerant evaporated in the evaporator 7 returns to the compressor 1.
Fig. 2 is a schematic structural diagram of a throttling device of a refrigerant circulation system according to the present embodiment. Referring to fig. 1 and 2, the throttling device of the present embodiment includes a refrigerant inlet 8, a refrigerant outlet 9, a throttling component 5, and a bypass pressure relief pipeline 6. The throttling device also comprises a main pipeline 4 which is communicated with the refrigerant inlet 8 and the throttling component 5.
The refrigerant inlet 8 of the throttling device is communicated with the outlet of the condenser 3, and the refrigerant outlet 9 is communicated with the inlet of the evaporator 7. The throttle 5 is located between the refrigerant inlet 8 and the refrigerant outlet 9 in the refrigerant flow direction.
The bypass pressure relief pipeline 6 is located between the refrigerant inlet 8 and the refrigerant outlet 9 in the refrigerant flowing direction and is connected in parallel with the throttling part 5 to balance the pressure upstream and downstream of the throttling part 5 after the refrigerant circulating system is stopped and the throttling part 5 is closed.
In this embodiment, after the refrigerant cycle system is stopped, the bypass pressure relief pipeline 6 can communicate the upstream pipeline of the throttling component 5 with the downstream pipeline of the throttling component 5, so as to solve the problem that the torque is too large at the moment of starting due to large pressure difference between the exhaust port and the suction port when the compressor is restarted.
In some embodiments, a control valve is disposed in the bypass pressure relief line 6, and the control valve is configured to open the bypass pressure relief line 6 to balance the pressure upstream and downstream of the throttling part 5 after the refrigerant cycle system is stopped and the throttling part 5 is closed. Preferably, the control valve comprises a solenoid valve.
The throttle member 5 comprises a throttle valve. The throttle valve is an electromagnetic expansion valve or a thermal expansion valve.
In some embodiments, the compressor is a single-phase rotor compressor, and frequent starting of the system after shutdown of the refrigerant circulation system using the single-phase rotor compressor is likely to cause the problem of overload protection of the compressor.
In some embodiments, the bypass pressure relief line 6 comprises a capillary tube.
As shown in fig. 3 to 5, the bypass pressure-releasing pipeline 6 includes a bent pipe section 61, the bent pipe section 61 is located at one end of the bypass pressure-releasing pipeline 6 adjacent to the refrigerant inlet 8, a section of the bypass pressure-releasing pipeline 6 adjacent to the inlet end is the bent pipe section 61, and the bent pipe section 61 is beneficial to reducing pipeline vibration caused by the increase of the flow rate after the refrigerant enters the bypass pressure-releasing pipeline 6, and is beneficial to improving the service life of the pipeline. In this embodiment, the pipe bending section 61 is formed in a semicircular shape having a diameter of 25 mm.
The bypass pressure relief line 6 also includes a coiled pipe section 63 in communication with the elbow section 61. After the high-pressure liquid refrigerant flows in the coiled pipe section 63 of the bypass pressure relief pipeline 6, at least part of the liquid refrigerant is gasified due to the reduction of the pressure, and finally enters the evaporator 7 through the refrigerant outlet 9. Further, coiling the pipeline into coil section 63 is also beneficial to improving the structural strength of the bypass pressure relief pipeline 6.
The coiled tube section 63 is coiled 1 to 3 times. Preferably, the coiled tubing section 63 is coiled 1.5 times. The bypass pressure relief pipeline 6 is excessively bent to cause overlarge throttling resistance to cause system low-pressure fluctuation, and the bypass pressure relief pipeline 6 is excessively large in occupied space to be scratched and broken due to excessively small bending.
In this embodiment, the coil section 63 encloses a circle having a diameter of 25 mm.
In some embodiments, the bypass pressure relief line 6 has an inner diameter of 3.03mm, an overall length of 300mm, and a wall thickness of 1.8 mm.
The throttling device further comprises a connecting pipe section 62, a first end of the connecting pipe section 62 is communicated with the bent pipe section 61, a second end of the connecting pipe section 62 is communicated with the coiled pipe section 63, and the bent pipe section 61 and the coiled pipe section 63 are arranged at intervals in the circumferential direction of the connecting pipe section 62.
As shown in fig. 2, in the present embodiment. The elbow section 61 is generally semicircular with the inlet and outlet of the elbow section 61 facing downward.
As shown in fig. 4, the bent tube section 61 and the coiled tube section 63 are spaced apart in the circumferential direction of the connection tube section 62 by an angle a, wherein the angle a is 60 to 80 degrees, preferably a is 76 degrees. The connecting pipe section 62 is connected to the outlet end of the bent pipe section 61 and extends toward the coiled pipe section 63 in a tangential direction of the bent pipe section 61; the connecting tube section 62 is connected to the inlet end of the coiled tube section 63 and extends toward the bent tube section 61 in a tangential direction of the coiled tube section 63.
The connecting tube section 62 extends in a vertical direction and is tangent to both the bent tube section 61 and the coiled tube section 63. The bent pipe section 61 and the coiled pipe section 63 are respectively located at both ends of the connection pipe section 62, and are spaced apart in the circumferential direction of the connection pipe section 62. That is, as shown in fig. 4, an angle a is formed between a plane in which the bent pipe section 61 is located and a plane in which the circular shape of the coiled pipe section 63 is enclosed.
According to another aspect of the present invention, the present embodiment further provides a refrigerant circulation system, which includes a compressor 1, a condenser 2, an evaporator 7, and the condenser 2 is communicated with an exhaust port of the compressor 1; the evaporator 7 comprises an inlet communicated with the condenser 2 and an outlet communicated with a suction port of the compressor 1; the throttle device is located between the condenser 2 and the evaporator 7 in the refrigerant flow direction. And a refrigerant inlet 8 of the throttling device is communicated with the condenser, and a refrigerant outlet 9 of the throttling device is communicated with the evaporator 7.
According to the utility model discloses an on the other hand, this embodiment still provides an air conditioner, and this air conditioner includes foretell refrigerant circulation system.
In summary, the throttling component is rapidly closed when the refrigerant circulation system is stopped, so that when the refrigerant circulation system is frequently started, the pressure difference between the air suction port and the air discharge port of the compressor is large, the torque is too large at the moment of starting, the starting current is too large to exceed the rated set current value of the compressor, and the overload protection phenomenon of the compressor occurs.
In view of the above problem, the present embodiment provides a throttling device, which includes a refrigerant inlet 8 communicated with the condenser 2, a refrigerant outlet 9 communicated with the evaporator 7, a throttling component 5 located between the refrigerant inlet 8 and the refrigerant outlet 9 along the refrigerant flowing direction, and a bypass pressure relief pipeline 6 connected in parallel with the throttling component 5. The bypass pressure relief pipeline 6 is communicated with a high-pressure side (positioned between an exhaust port of the compressor 1 and the throttling component 5) and a low-pressure side (positioned between the throttling component 5 and an air suction port of the compressor 1) of the refrigerant circulating system, so that the pressure difference between the exhaust port and the air suction port of the compressor 1 is reduced, and the overload protection of the compressor caused by overlarge pressure at the moment of starting is improved.
When the refrigerant circulating system normally operates, the throttling component 5 is normally opened, the high-temperature high-pressure liquid refrigerant is divided into two paths through the refrigerant inlet of the throttling device, one path of refrigerant is throttled and depressurized through the throttling component 5 to form low-temperature low-pressure gas-liquid mixed refrigerant, the low-temperature low-pressure gas-liquid mixed refrigerant enters the evaporator 7 to be evaporated and heat exchanged and then is changed into low-temperature low-pressure gaseous refrigerant, and then the low-temperature low-pressure gaseous refrigerant enters the air suction port of the compressor 1. The other path is slightly throttled from a bypass pressure relief pipeline 6 without passing through a throttling component 5 and then is merged into a throttled main pipeline; at this time, the opening degree of the throttling component 5 needs to be reduced to match the system operation because the flow rate of the refrigerant flowing into the throttling component is reduced; therefore, the bypass pressure relief pipeline 6 can increase the cooling capacity range of the throttling component 5, and can adapt to the working conditions of the harsher environment.
When the refrigerant circulating system is stopped, the throttling part 5 is quickly closed, the pressure before throttling is close to the exhaust pressure, the pressure after throttling is close to the evaporation pressure, at the moment, the high-pressure side pressure can be quickly bypassed to the low-pressure side, so that the refrigerant circulating system can balance high pressure and low pressure in a short time (within three minutes), and after the refrigerant circulating system is immediately started after being stopped, the single-phase compressor is naturally and safely started after three minutes.
The system has strict requirements on the capillary tube, the capillary tube is not easy to be thicker and longer, and the number of turns of winding is not easy to be more; poor bypass capillary matching can lead to air conditioner performance fluctuations. For a 5kW single-phase rotor compressor air conditioner, a TP2M capillary tube with the diameter of 3.03mm (pipe diameter) multiplied by 1.8mm (pipe wall thickness) multiplied by 300mm (pipe length) is arranged to enable the time of balancing high and low pressure sides to be stabilized within three minutes so as to comply with the three-control logic of unit start, six stops, and after the capillary tube is arranged with the length of 300mm and wound for 1.5 circles, the bypass flow of the system increases the evaporation temperature of the system and simultaneously can not cause system pressure fluctuation.
Simulation data: when no bypass capillary tube is arranged, the high-low pressure balance time of the system after frequent starting is 9 minutes; when a bypass capillary tube of TP2M phi 2 (tube diameter) multiplied by 700mm (tube length) is matched, the high-low pressure balance time of the system after frequent starting is 6 minutes; when a bypass capillary tube of TP2M phi 2 (tube diameter) multiplied by 500 (tube length) is matched, the high-low pressure balance time of the system after frequent starting is 6 minutes; when a bypass capillary tube of TP2M phi 2 (tube diameter) multiplied by 200 (tube length) is matched, the high-low pressure balance time of the system after frequent starting is 6 minutes; when the bypass capillary tube of TP2M Ph 3.03 (tube diameter) multiplied by 300 (tube length) is matched, the high-low pressure balance time of the system after frequent starting is 3 minutes.
The refrigerant passes through an inlet of the capillary tube and then passes through an upward half circle (the bent tube section 61), an included angle between the bent tube section 61 and the coiling section 63 is 76 degrees, the aim is to relieve the stress of a pipeline caused by transverse and longitudinal vibration due to the increase of flow velocity after sudden change of the tube diameter through half bending and swing angle digestion, the service life of the pipeline is reasonably protected, after the high-pressure refrigerant capillary tube is bent around for 1.5 circles, part of liquid refrigerant is just vaporized after reasonable pressure drop, and finally the liquid refrigerant is mixed into an air suction pipeline in a gas-liquid mixed state, meanwhile, the fixing firmness degree of the capillary tube is enhanced, and the purpose of bypassing is reasonably and effectively achieved; too much bending can cause too much throttling resistance to cause low-pressure fluctuation of the system, and too little bending can cause too much occupied space of the capillary tube to be scratched and broken.
The above description is only exemplary embodiments of the present invention, and should not be construed as limiting the present invention, and any modifications, equivalent replacements, improvements, etc. made within the spirit and principle of the present invention should be included in the protection scope of the present invention.
Claims (10)
1. A throttle device of a refrigerant cycle system, comprising:
a refrigerant inlet (8);
a refrigerant outlet (9);
the throttling component (5) is positioned between the refrigerant inlet (8) and the refrigerant outlet (9) along the refrigerant flowing direction; and
and the bypass pressure relief pipeline (6) is positioned between the refrigerant inlet (8) and the refrigerant outlet (9) along the refrigerant flowing direction and is connected with the throttling component (5) in parallel, so that the upstream pressure and the downstream pressure of the throttling component (5) are balanced after the refrigerant circulating system is stopped and the throttling component (5) is closed.
2. The throttle device of claim 1,
the bypass pressure relief pipeline (6) comprises a capillary tube; or
And a control valve is arranged in the bypass pressure relief pipeline (6).
3. A throttle device according to claim 1, characterized in that the bypass pressure relief line (6) comprises a bend (61), said bend (61) being located at an end of the bypass pressure relief line (6) adjacent to the refrigerant inlet (8).
4. A restriction device according to claim 3, wherein the bypass pressure relief line (6) further comprises a coiled pipe section (63) communicating with the pipe bend section (61).
5. A throttle device according to claim 4, characterized in that the coiled pipe section (63) is coiled 1 to 3 times.
6. The throttle device according to claim 4, further comprising a connecting pipe section (62), wherein a first end of the connecting pipe section (62) is communicated with the bent pipe section (61), a second end of the connecting pipe section (62) is communicated with the coiled pipe section (63), and the bent pipe section (61) and the coiled pipe section (63) are arranged at intervals in a circumferential direction of the connecting pipe section (62).
7. A restriction device according to claim 6, wherein the bent tube section (61) and the coiled tube section (63) are circumferentially spaced apart by an angle a of 60 to 80 degrees in the connecting tube section (62).
8. Throttling device according to claim 6,
the connecting pipe section (62) is connected with the outlet end of the bent pipe section (61) and extends towards the coiled pipe section (63) along the tangential direction of the bent pipe section (61);
the connecting pipe section (62) is connected with the inlet end of the coiled pipe section (63) and extends towards the bent pipe section (61) along the tangential direction of the coiled pipe section (63).
9. A refrigerant circulation system, comprising:
a compressor (1);
a condenser (2) in communication with an exhaust port of the compressor (1);
an evaporator (7) comprising an inlet in communication with the condenser (2) and an outlet in communication with a suction inlet of the compressor (1); and
a throttle device according to any one of claims 1 to 8, located between said condenser (2) and said evaporator (7) in the direction of refrigerant flow.
10. An air conditioner comprising the refrigerant circulation system according to claim 9.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202022283756.5U CN213178585U (en) | 2020-10-14 | 2020-10-14 | Throttling device of refrigerant circulation system, refrigerant circulation system and air conditioner |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202022283756.5U CN213178585U (en) | 2020-10-14 | 2020-10-14 | Throttling device of refrigerant circulation system, refrigerant circulation system and air conditioner |
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| Publication Number | Publication Date |
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| CN213178585U true CN213178585U (en) | 2021-05-11 |
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| Application Number | Title | Priority Date | Filing Date |
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| CN202022283756.5U Active CN213178585U (en) | 2020-10-14 | 2020-10-14 | Throttling device of refrigerant circulation system, refrigerant circulation system and air conditioner |
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| CN (1) | CN213178585U (en) |
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