CN108716763B - Air conditioner - Google Patents
Air conditioner Download PDFInfo
- Publication number
- CN108716763B CN108716763B CN201810430165.0A CN201810430165A CN108716763B CN 108716763 B CN108716763 B CN 108716763B CN 201810430165 A CN201810430165 A CN 201810430165A CN 108716763 B CN108716763 B CN 108716763B
- Authority
- CN
- China
- Prior art keywords
- length
- inner diameter
- liquid supply
- compressor
- supply pipe
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Active
Links
Images
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F13/00—Details common to, or for air-conditioning, air-humidification, ventilation or use of air currents for screening
- F24F13/30—Arrangement or mounting of heat-exchangers
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F5/00—Air-conditioning systems or apparatus not covered by F24F1/00 or F24F3/00, e.g. using solar heat or combined with household units such as an oven or water heater
- F24F5/0007—Air-conditioning systems or apparatus not covered by F24F1/00 or F24F3/00, e.g. using solar heat or combined with household units such as an oven or water heater cooling apparatus specially adapted for use in air-conditioning
- F24F5/001—Compression cycle type
Abstract
The invention discloses an air conditioner, which comprises a compressor, a first heat exchanger, a second heat exchanger, a throttling device and a heat regenerator, wherein the heat regenerator comprises a liquid supply pipe and an air return pipe; an inlet of the liquid supply pipe is connected with an outlet of the first heat exchanger, and an outlet of the liquid supply pipe is connected with an inlet of the throttling device; an inlet of the air return pipe is connected with an outlet of the second heat exchanger, and an outlet of the air return pipe is connected with an inlet of the compressor; one or more of the length of the liquid supply pipe, the length of the air return pipe, the difference Δ l1 between the inner diameter of the outlet of the liquid supply pipe and the inner diameter of the inlet of the liquid supply pipe, the difference Δ l2 between the inner diameter of the inlet of the air return pipe and the inner diameter of the outlet of the air return pipe and the operating frequency of the compressor are in a correlation relationship with the structural parameters of the throttling device. The invention ensures that the power of the throttling device is matched with that of the air conditioner, avoids low heat exchange efficiency and high energy consumption caused by improper selection of the throttling device, and accelerates the regulation rate of the air conditioner to the indoor temperature.
Description
Technical Field
The invention relates to the technical field of electric appliances, in particular to an air conditioner.
Background
With the development of economy and the advancement of technology, users have higher and higher performance requirements on air conditioners. The refrigeration loop of the traditional air conditioner usually comprises a compressor, a condenser, a throttling device and an evaporator which are connected together, heat exchange is carried out between the condenser and ambient air through the evaporator, the heat exchange effect is general, the supercooling degree is not high, and the requirement of a user can not be well met. The prior art discloses an air conditioning system including a heat regenerator, an outlet of a compressor is connected to an inlet of the condenser, an outlet of the condenser is connected to an inlet of a throttling device, an outlet of the throttling device is connected to an inlet of an inner tube of the heat regenerator, an outlet of the inner tube of the heat regenerator is connected to an inlet of an evaporator, an outlet of an outer cavity of the heat regenerator is connected to an inlet of the compressor, an inlet of the outer cavity of the heat regenerator is connected to an outlet of the evaporator, and an outlet of the evaporator is connected to an inlet of the compressor. Air conditioning systems disclosed in the prior art exchange heat between low-temperature and low-pressure refrigerant from an evaporator and high-temperature and high-pressure refrigerant from a condenser in a heat regenerator to improve heat exchange efficiency. However, the throttling device of the air conditioner is determined according to the matching requirement of the air conditioner, and after the heat regenerator is additionally arranged in the air conditioning system disclosed by the prior art, the structural parameters of the throttling device are not adjusted, so that the refrigerating capacity of the air conditioning device is reduced to a certain extent, and the energy consumption is improved.
Disclosure of Invention
The embodiment of the invention provides an air conditioner, and aims to solve the problems that in the prior art, a throttling device is not matched with the air conditioner, the refrigerating capacity of the air conditioner is reduced, and the energy consumption of the air conditioner is improved. The following presents a simplified summary in order to provide a basic understanding of some aspects of the disclosed embodiments. This summary is not an extensive overview and is intended to neither identify key/critical elements nor delineate the scope of such embodiments. Its sole purpose is to present some concepts in a simplified form as a prelude to the more detailed description that is presented later.
The embodiment of the invention provides an air conditioner, which comprises a compressor, a first heat exchanger, a second heat exchanger, a throttling device and a heat regenerator, wherein the heat regenerator comprises a liquid supply pipe and a gas return pipe; an inlet of the liquid supply pipe is connected with an outlet of the first heat exchanger, and an outlet of the liquid supply pipe is connected with an inlet of the throttling device; an inlet of the air return pipe is connected with an outlet of the second heat exchanger, and an outlet of the air return pipe is connected with an inlet of the compressor; one or more of the length of the liquid supply pipe, the length of the air return pipe, the difference Δ l1 between the inner diameter of the outlet of the liquid supply pipe and the inner diameter of the inlet of the liquid supply pipe, the difference Δ l2 between the inner diameter of the inlet of the air return pipe and the inner diameter of the outlet of the air return pipe and the operating frequency of the compressor are in a correlation relationship with the structural parameters of the throttling device.
Optionally, the throttling device is a capillary tube; the structural parameters of the throttling device comprise: the inner diameter of the capillary, the length of the capillary, or both.
Optionally, the length of the liquid supply pipe, the length of the air return pipe and the working frequency of the compressor have a first correlation with the inner diameter of the capillary pipe; the first association relationship is:
wherein R1 is the inner diameter of the capillary; h1 is the length of the liquid supply pipe; h2 is the return air pipe length; p is the working frequency of the compressor; and a and b are inner diameter adjustment coefficients of the capillary.
Alternatively to this, the first and second parts may,
the length of the liquid supply pipe, the length of the air return pipe and the working frequency of the compressor have a second correlation with the length of the capillary pipe; the second correlation is as follows:
L1＝c×(h1+h2)+d×P
wherein L1 is the length of the capillary; h1 is the length of the liquid supply pipe; h2 is the return air pipe length; p is the working frequency of the compressor; c and d are the length adjustment coefficients of the capillary.
Optionally, the difference Δ l1, the difference Δ l2 and the operating frequency of the compressor have a third correlation with the inner diameter of the capillary tube; the third relationship is as follows:
wherein R2 is the inner diameter of the capillary; p is the working frequency of the compressor; and m and n are inner diameter adjusting coefficients of the capillary.
Optionally, the difference Δ l1, the difference Δ l2 and the operating frequency of the compressor have a fourth correlation with the length of the capillary tube; the fourth correlation is as follows:
wherein L2 is the length of the capillary; p is the working frequency of the compressor; s and t are the capillary length adjustment coefficients.
Optionally, the inner diameter of the capillary tube is 1 mm-2 mm. Optionally, the capillary has an internal diameter of 1mm, 1.5mm or 2 mm.
Optionally, the length of the capillary tube is 400 mm-900 mm. Optionally, the capillary has a length of 400mm, 450mm, 500mm, 550mm, 600mm, 650mm, 700mm, 750mm, 800mm, 850mm or 900 mm.
Optionally, the liquid supply tube further comprises: the fin structure is arranged on the outer wall of the liquid supply pipe; the muffler still includes: and the fin structure is arranged on the outer wall of the air return pipe.
Optionally, the liquid supply pipe and the air return pipe are coupled to each other or the air return pipe is sleeved outside the liquid supply pipe.
Optionally, the liquid supply tube further comprises: a thermally conductive coating; the thermal conductivity of the thermal conductive coating is greater than the thermal conductivity of the liquid supply tube; the muffler still includes: a thermally conductive coating; the heat conductivity coefficient of the heat-conducting coating is larger than that of the air return pipe.
The technical scheme provided by the embodiment of the invention has the following beneficial effects:
the air conditioner provided by the embodiment of the invention comprises a compressor, a first heat exchanger, a second heat exchanger, a throttling device and a heat regenerator, wherein the heat regenerator comprises a liquid supply pipe and an air return pipe, and the heat exchange speed of the air conditioner is improved.
It is to be understood that both the foregoing general description and the following detailed description are exemplary and explanatory only and are not restrictive of the invention, as claimed.
Drawings
The accompanying drawings, which are incorporated in and constitute a part of this specification, illustrate embodiments consistent with the invention and together with the description, serve to explain the principles of the invention.
Fig. 1 is a schematic structural view illustrating an air conditioner according to an exemplary embodiment;
FIG. 2a is a schematic illustration showing a positional distribution of a supply tube and an air return tube in accordance with an exemplary embodiment;
fig. 2b is a schematic illustration of a positional distribution of a supply tube and an air return tube according to an exemplary embodiment.
Detailed Description
The following description and the drawings sufficiently illustrate specific embodiments of the invention to enable those skilled in the art to practice them. Portions and features of some embodiments may be included in or substituted for those of others. The scope of embodiments of the invention encompasses the full ambit of the claims, as well as all available equivalents of the claims. Herein, relational terms such as first and second, and the like may be used solely to distinguish one entity or structure from another entity or structure without requiring or implying any actual such relationship or order between such entities or structures. The embodiments are described in a progressive manner, each embodiment focuses on differences from other embodiments, and the same and similar parts among the embodiments are referred to each other.
In the description of the present invention, it is to be understood that the terms "longitudinal", "lateral", "upper", "lower", "front", "rear", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer", and the like, indicate orientations or positional relationships based on those shown in the drawings, and are used merely for convenience of description and for simplicity of description, and do not indicate or imply that the referenced devices or elements must have a particular orientation, be constructed in a particular orientation, and be operated, and thus, are not to be construed as limiting the present invention. In the description of the present invention, unless otherwise specified and limited, it is to be noted that the terms "mounted," "connected," and "connected" are to be interpreted broadly, and may be, for example, a mechanical connection or an electrical connection, a communication between two elements, a direct connection, or an indirect connection via an intermediate medium, and specific meanings of the terms may be understood by those skilled in the art according to specific situations.
The air conditioner provided by the embodiment of the invention is a wall-mounted air conditioner, a vertical cabinet air conditioner or a window type air conditioner, mainly aims at the window type air conditioner, the traditional air conditioner is provided with a compressor, a first heat exchanger, a second heat exchanger and a throttling device, the wall-mounted air conditioner and the vertical cabinet air conditioner structurally comprise an indoor unit and an outdoor unit, when the heat regenerator is additionally arranged, different factors in the indoor unit and the outdoor unit need to be integrated and compared to determine that the heat regenerator is arranged in the indoor unit or the outdoor unit, and for the window type air conditioner, the structure is simple, and when the heat regenerator.
As shown in fig. 1, the air conditioner provided by the present invention includes a compressor 1, a first heat exchanger 2, a second heat exchanger 3, a throttling device 4, and a heat regenerator 5, wherein the heat regenerator 5 includes a liquid supply pipe 51 and a gas return pipe 52. An inlet of the liquid supply pipe 51 is connected with an outlet of the first heat exchanger 2, an outlet of the liquid supply pipe 51 is connected with an inlet of the throttling device 4, an inlet of the gas return pipe 52 is connected with an outlet of the second heat exchanger 3, and an outlet of the gas return pipe 52 is connected with an inlet of the compressor 1, wherein one or more of the length of the liquid supply pipe 51, the length of the gas return pipe 52, the difference delta l1 between the inner diameter of the outlet of the liquid supply pipe 51 and the inner diameter of the inlet of the gas return pipe 52, the difference delta l2 between the inner diameter of the outlet of the gas return pipe 52 and the operating frequency of the compressor 1 has an associated relation with the structural parameters of the throttling device 4.
The working principle of the embodiment is as follows: refrigerant gas is sucked by the compressor 1 and then is pressurized to be changed into high-temperature and high-pressure refrigerant gas, the high-temperature and high-pressure refrigerant gas flows to the first heat exchanger 2, is released in the first heat exchanger 2 and is changed into normal-temperature and high-pressure liquid and flows to the heat regenerator 5, and the high-temperature and high-pressure refrigerant gas enters the throttling device 4 to be throttled and depressurized to be changed into low-temperature and low-pressure liquid after being released by the heat regenerator 5. The low-temperature and low-pressure liquid refrigerant flows to the second heat exchanger 3, absorbs heat in the second heat exchanger 3, evaporates, and turns into a low-temperature and low-pressure gas. The refrigerant gas of low temperature and low pressure flows through the regenerator 5, is heated after passing through the regenerator 5, is sucked by the compressor 1, and circulates.
Wherein, first heat exchanger 2 is as the condenser, and second heat exchanger 3 is as the evaporimeter, and the low temperature low pressure gaseous state refrigerant that the evaporimeter came out carries out the heat exchange with the normal atmospheric temperature high pressure liquid refrigerant that puts that the condenser came out in regenerator 5 can improve compressor 1's efficiency, prevents the liquid hammer, has improved the heat exchange efficiency of air conditioner simultaneously, has reduced the energy consumption.
The air conditioner has various types, models and power, and in order to ensure that the air conditioner can achieve an ideal refrigeration effect, avoid short-time abrasion caused by excessive pressure borne by the throttling device 4 due to improper selection of the throttling device 4 and shorten the service life of the air conditioner, the working frequency of the compressor 1 has an incidence relation with the structural parameters of the throttling device 4. In the embodiment of the invention, in the manufacturing process of the air conditioner, the proper throttling device 4 is selected according to the working frequency of the compressor 1, the effective circulation of the refrigerant is ensured, the ideal refrigeration effect is achieved, and meanwhile, the throttling device 4 bears the proper pressure, so that the service life of the air conditioner is prolonged. The operating frequency of the compressor 1 directly determines the rate of change of state of the refrigerant, and the flow rate of the refrigerant. In some alternative embodiments, the compressor 1 is a fixed-frequency compressor, and the suitable throttling device 4 is selected directly according to the rated working frequency of the compressor 1. In some alternative embodiments, the compressor 1 is an inverter compressor, and in order to avoid wear caused by excessive pressure applied to the throttling device 4, a suitable throttling device 4 is selected according to the maximum operating frequency of the compressor 1. In some alternative embodiments, the compressor 1 is an inverter compressor, and in order to ensure the long-term effective operation of the air conditioner, the appropriate throttling device 4 is selected according to the average value of the minimum operating frequency and the maximum operating frequency of the compressor 1.
Optionally, the throttling device 4 is a capillary tube or an expansion valve. When the throttling device 4 is a capillary tube, the correlation between the working frequency of the compressor 1 and the structural parameters of the throttling device 4 includes: the working frequency of the compressor 1 has a correlation with the inner diameter, length or wall thickness of the capillary tube; when the throttling device 4 is an expansion valve, the correlation between the working frequency of the compressor 1 and the structural parameters of the throttling device 4 comprises: the operating frequency of the compressor 1 has a correlation with the drift diameter of the expansion valve, the inner diameter of the nozzle inlet, the inner diameter of the nozzle outlet, or the like.
Wherein, the difference Δ l1 between the inner diameter of the outlet of the liquid supply pipe 51 minus the inner diameter of the inlet of the liquid supply pipe 51 and the difference Δ l2 between the inner diameter of the inlet of the gas return pipe 52 minus the inner diameter of the outlet of the gas return pipe 52 are both greater than or equal to zero. In some alternative embodiments, the inner diameters of the supply tube 51 and the return tube 52 are constant to facilitate the manufacture of the supply tube 51 and the return tube 52. In some alternative embodiments, to improve heat exchange efficiency, the inner diameters of the liquid supply pipe 51 and the gas return pipe 52 are increased or decreased as the state of the refrigerant is changed. For example, in the liquid supply pipe 51, the refrigerant is vaporized from liquid to gas in a heat absorption manner as the heat exchange process proceeds, and the volume is increased, so that the inner diameter of the outlet of the liquid supply pipe 51 is larger than the inner diameter of the inlet of the liquid supply pipe 51, and the difference Δ l1 is larger than zero. Similarly, in the gas return pipe 52, as the heat exchange process proceeds, the refrigerant is liquefied from a gaseous state to a liquid state, and the volume is reduced, so the inner diameter of the inlet of the gas return pipe 52 is larger than the inner diameter of the outlet of the gas return pipe 52, and the difference Δ l2 is larger than zero.
In addition, in the embodiment of the invention, the reflux device 5 is additionally arranged, the reflux device 5 has the function of improving the heat exchange efficiency of the air conditioner, meanwhile, the proper throttling device 4 is selected for the rated working frequency of the compressor 1, and meanwhile, the throttling device 4 is selected for the relevant parameters of the reflux device 5, so that the pressure born by the throttling device 4 can be reduced, the service life of the air conditioner is prolonged, meanwhile, the throttling device 4 is selected for the comprehensive multiple factors, the refrigeration efficiency of the air conditioner is further improved, and the energy consumption is saved. Specifically, the throttle device 4 is selected according to one or more of the length of the supply pipe 51, the length of the return pipe 52, the difference Δ l1 between the inner diameter of the outlet of the supply pipe 51 and the inner diameter of the inlet of the supply pipe 51, the difference Δ l2 between the inner diameter of the inlet of the return pipe 52 and the inner diameter of the outlet of the return pipe 52, and the operating frequency of the compressor 1.
The air conditioner provided by the embodiment of the invention comprises a compressor, a first heat exchanger, a second heat exchanger, a throttling device and a heat regenerator, wherein the heat regenerator comprises a liquid supply pipe and an air return pipe, and the heat exchange speed of the air conditioner is improved.
In some alternative embodiments, when the air conditioner is a window air conditioner, a capillary tube is used as the throttling device 4. When the throttling device 4 is a capillary tube, the structural parameters of the throttling device 4 include: the inner diameter of the capillary, the length of the capillary, or both.
In some embodiments, the length of the supply tube 51, the length of the return tube 52 and the operating frequency of the compressor 1 have a first relationship with the inner diameter of the capillary tube, in particular, the first relationship is as follows:
wherein R1 is the inner diameter of the capillary; h1 is the length of the supply tube 51; h2 is the length of muffler 52; p is the operating frequency of the compressor 1; and a and b are inner diameter adjustment coefficients of the capillary.
In some alternative embodiments, the length of the supply pipe 51, the length of the return pipe 52 and the operating frequency of the compressor 1 have a second correlation with the length of the capillary tube, in particular, the second correlation is as follows:
l1 ═ c × (h1+ h2) + d × P formula (2)
Wherein L1 is the length of the capillary; h1 is the length of the supply tube 51; h2 is the length of muffler 52; p is the operating frequency of the compressor 1; c and d are the length adjustment coefficients of the capillary.
In some embodiments, the length of the supply tube 51, the length of the return air tube 52, and the operating frequency of the compressor are associated with the inner diameter of the capillary tube as in equation (1) above, and the length of the supply tube 51, the length of the return air tube 52, and the operating frequency of the compressor 1 are associated with the length of the capillary tube as in equation (2) above.
In some embodiments, the difference Δ l1 between the inner diameter of the outlet of the supply pipe 51 minus the inner diameter of the inlet of the supply pipe 51, the difference Δ l2 between the inner diameter of the inlet of the return pipe 52 minus the inner diameter of the outlet of the return pipe 52, and the operating frequency of the compressor 1 have a third relationship with the inner diameter of the capillary tube, specifically, the third relationship is as follows:
wherein R2 is the inner diameter of the capillary; p is the operating frequency of the compressor 1; m and n are inner diameter adjusting coefficients of the capillary; Δ l1 and Δ l2 are greater than or equal to zero.
In some embodiments, the difference Δ l1 between the inner diameter of the outlet of the supply pipe 51 minus the inner diameter of the inlet of the supply pipe 51, the difference Δ l2 between the inner diameter of the inlet of the return pipe 52 minus the inner diameter of the outlet of the return pipe 52, and the operating frequency of the compressor 1 have a fourth correlation with the length of the capillary tube, specifically, the fourth correlation is as follows:
wherein L2 is the length of the capillary; p is the operating frequency of the compressor 1; s and t are the length adjustment coefficients of the capillary; Δ l1 and Δ l2 are greater than or equal to zero.
In some embodiments, the difference Δ l1 between the inner diameter of the outlet of the supply pipe 51 minus the inner diameter of the inlet of the supply pipe 51, the difference Δ l2 between the inner diameter of the inlet of the muffler 52 minus the inner diameter of the outlet of the muffler 52, and the operating frequency of the compressor 1 have a correlation with the inner diameter of the capillary tube as in the above formula (3). The difference Δ l1 between the inner diameter of the outlet of the supply pipe 51 minus the inner diameter of the inlet of the supply pipe 51, the difference Δ l2 between the inner diameter of the inlet of the muffler 52 minus the inner diameter of the outlet of the muffler 52, and the operating frequency of the compressor 1 have a correlation with the length of the capillary tube as in the above equation (4).
In some embodiments, the inner diameters of the capillary tubes, R1 and R2, are determined according to equations (1) and (3) above, respectively, and the average of R1 and R2 is taken to determine the inner diameter of the capillary tube from the average.
In some embodiments, lengths of the capillary tube, L1 and L2, are determined according to equations (2) and (4) above, respectively, and the average of L1 and L2 is taken, from which the length of the capillary tube is determined.
In some embodiments, the inner diameters of the capillary tubes, R1 and R2, are determined according to equations (1) and (3) above, respectively, and the average of R1 and R2 is taken to determine the inner diameter of the capillary tube from the average. The lengths of the capillary tubes L1 and L2 were determined according to the above equations (2) and (4), respectively, and the average values of L1 and L2 were found, and the lengths of the capillary tubes were determined from the average values. And the structural parameters of the throttling device 4 are determined by integrating the incidence relations between various factors and the throttling device 4, so that the effectiveness of improving the heat exchange efficiency of the air conditioner is ensured.
The length of the capillary tube determined according to the previous embodiment is 400mm to 900 mm. The inner diameter of the capillary tube is 1 mm-1.5 mm. Generally, the length of the capillary tube is 500 mm-2000 mm, and the volume of the air conditioner is not too large easily, and at the moment, when the length of the capillary tube exceeds 1000mm, the capillary tube needs to be bent for many times, so that the flow velocity of a refrigerant is influenced, and the heat exchange efficiency of the air conditioner is reduced. In the embodiment of the invention, after the heat exchanger 5 is additionally arranged, the capillary tube works with the capillary tube, so that the length of the capillary tube is shortened, the capillary tube is prevented from being bent for many times to reduce the flow velocity of the refrigerant, and the heat exchange efficiency of the air conditioner is improved.
In some alternative embodiments, in order to increase the heat exchange rate of the refrigerant in the regenerator 5, further improve the efficiency of the compressor 1, and effectively prevent liquid slugging, the outer walls of the liquid supply pipe 51 and the gas return pipe 52 both include fin structures.
In the foregoing embodiments, the supply pipe 51 and the return pipe 52 are disposed in various manners, and in some alternative embodiments, as shown in fig. 2a, the supply pipe 51 and the return pipe 52 are coupled. In some alternative embodiments, as shown in fig. 2b, the air return pipe 52 is sleeved outside the liquid supply pipe 51. Preferably, in this embodiment, in order to increase the heat exchange rate between the liquid supply pipe 51 and the air return pipe 52, the air return pipe 52 is sleeved outside the liquid supply pipe 51.
In some optional embodiments, in order to increase the heat exchange rate of the refrigerant in the heat regenerator 5, further improve the efficiency of the compressor 1, and effectively prevent liquid slugging, the outer walls of the liquid supply pipe 51 and the gas return pipe 52 are further coated with heat conductive coatings, respectively, and the heat conductivity coefficient of the heat conductive coatings is greater than that of the liquid supply pipe 51 and the gas return pipe 52.
The present invention is not limited to the structures that have been described above and shown in the drawings, and various modifications and changes can be made without departing from the scope thereof. The scope of the invention is limited only by the appended claims.
Claims (8)
1. An air conditioner comprises a compressor, a first heat exchanger, a second heat exchanger, a throttling device and a heat regenerator, and is characterized in that the heat regenerator comprises a liquid supply pipe and a gas return pipe; an inlet of the liquid supply pipe is connected with an outlet of the first heat exchanger, and an outlet of the liquid supply pipe is connected with an inlet of the throttling device; an inlet of the air return pipe is connected with an outlet of the second heat exchanger, and an outlet of the air return pipe is connected with an inlet of the compressor; one or more of the length of the liquid supply pipe, the length of the air return pipe, the difference Δ l1 between the inner diameter of the outlet of the liquid supply pipe and the inner diameter of the inlet of the liquid supply pipe, the difference Δ l2 between the inner diameter of the inlet of the air return pipe and the inner diameter of the outlet of the air return pipe and the operating frequency of the compressor are in a correlation relationship with the structural parameters of the throttling device;
the throttling device is a capillary tube; the structural parameters of the throttling device comprise: one or both of an inner diameter of the capillary tube and a length of the capillary tube;
the length of the liquid supply pipe, the length of the air return pipe and the working frequency of the compressor have a first correlation with the inner diameter of the capillary pipe; the first association relationship is:
wherein R1 is the inner diameter of the capillary; h1 is the length of the liquid supply pipe; h2 is the return air pipe length; p is the working frequency of the compressor; and a and b are inner diameter adjustment coefficients of the capillary.
2. The air conditioner of claim 1, wherein said liquid supply tube length, said return tube length and an operating frequency of said compressor have a second relationship with a length of said capillary tube; the second correlation is as follows:
L1＝c×(h1+h2)+d×P；
wherein L1 is the length of the capillary; h1 is the length of the liquid supply pipe; h2 is the return air pipe length; p is the working frequency of the compressor; c and d are the length adjustment coefficients of the capillary.
3. The air conditioner as claimed in claim 1, wherein the difference al 1, the difference al 2 and the operating frequency of the compressor have a third correlation with the inner diameter of the capillary tube; the third relationship is as follows:
wherein R2 is the inner diameter of the capillary; p is the working frequency of the compressor; and m and n are inner diameter adjusting coefficients of the capillary.
4. The air conditioner as claimed in claim 1, wherein the difference al 1, the difference al 2 and the operating frequency of the compressor have a fourth correlation with the length of the capillary tube; the fourth correlation is as follows:
wherein L2 is the length of the capillary; p is the working frequency of the compressor; s and t are the capillary length adjustment coefficients.
5. The air conditioner according to claim 1, wherein the capillary tube has an inner diameter of 1mm to 1.5 mm.
6. The air conditioner according to claim 1, wherein the capillary tube has a length of 400mm to 900 mm.
7. The air conditioner as claimed in claim 1, wherein the liquid supply pipe further comprises: the fin structure is arranged on the outer wall of the liquid supply pipe; the muffler still includes: and the fin structure is arranged on the outer wall of the air return pipe.
8. The air conditioner as claimed in claim 1, wherein the liquid supply pipe is coupled to the air return pipe or the air return pipe is sleeved outside the liquid supply pipe.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201810430165.0A CN108716763B (en) | 2018-05-08 | 2018-05-08 | Air conditioner |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201810430165.0A CN108716763B (en) | 2018-05-08 | 2018-05-08 | Air conditioner |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN108716763A CN108716763A (en) | 2018-10-30 |
| CN108716763B true CN108716763B (en) | 2020-09-25 |
Family
ID=63899515
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201810430165.0A Active CN108716763B (en) | 2018-05-08 | 2018-05-08 | Air conditioner |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN108716763B (en) |
Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1862151A (en) * | 2005-05-12 | 2006-11-15 | 乐金电子(天津)电器有限公司 | Air conditioner for regenerative cooling circulation system |
| JP2011208882A (en) * | 2010-03-30 | 2011-10-20 | Topre Corp | Gas-liquid heat exchange-type refrigerating device |
| CN202734081U (en) * | 2012-08-22 | 2013-02-13 | 海尔集团公司 | Air conditioner |
| CN203443182U (en) * | 2013-08-14 | 2014-02-19 | Tcl空调器(中山)有限公司 | Air conditioner |
| CN206257837U (en) * | 2016-09-28 | 2017-06-16 | 合肥华凌股份有限公司 | The muffler and refrigerating plant of refrigerating plant |
| CN107166594A (en) * | 2017-06-19 | 2017-09-15 | 青岛海尔空调器有限总公司 | A kind of air conditioner, control method and control device |
-
2018
- 2018-05-08 CN CN201810430165.0A patent/CN108716763B/en active Active
Patent Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1862151A (en) * | 2005-05-12 | 2006-11-15 | 乐金电子(天津)电器有限公司 | Air conditioner for regenerative cooling circulation system |
| JP2011208882A (en) * | 2010-03-30 | 2011-10-20 | Topre Corp | Gas-liquid heat exchange-type refrigerating device |
| CN202734081U (en) * | 2012-08-22 | 2013-02-13 | 海尔集团公司 | Air conditioner |
| CN203443182U (en) * | 2013-08-14 | 2014-02-19 | Tcl空调器(中山)有限公司 | Air conditioner |
| CN206257837U (en) * | 2016-09-28 | 2017-06-16 | 合肥华凌股份有限公司 | The muffler and refrigerating plant of refrigerating plant |
| CN107166594A (en) * | 2017-06-19 | 2017-09-15 | 青岛海尔空调器有限总公司 | A kind of air conditioner, control method and control device |
Also Published As
| Publication number | Publication date |
|---|---|
| CN108716763A (en) | 2018-10-30 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN102141274B (en) | Split air-conditioner | |
| CN107014015A (en) | Recovery type heat evaporating condensation type handpiece Water Chilling Units | |
| GB2415768A (en) | Improvement system of energy efficiency for refrigeration cycle | |
| CN108361884A (en) | Air-conditioning system | |
| WO2022068950A1 (en) | Room temperature adjusting device | |
| CN103743020A (en) | Dual-temperature radiation household air-conditioner capable of processing fresh air | |
| CN203605512U (en) | Air-cooling type compression condensing unit with supercooled gas-liquid separator | |
| CN215991717U (en) | Phase-change refrigerating system | |
| CN206669949U (en) | Recovery type heat evaporating condensation type handpiece Water Chilling Units | |
| CN108716763B (en) | Air conditioner | |
| CN208108567U (en) | Dispenser and air conditioner | |
| CN103174450B (en) | Mine air conditioner | |
| CN206504429U (en) | Unit dual temperature pump type heat thermostatic and humidistatic air conditioning unit group | |
| CN205779563U (en) | A kind of automobile air conditioner compressor | |
| CN102305496B (en) | Air-cooled heat pump unit | |
| CN103743171B (en) | A kind of heat pump air conditioner refrigerant quality compensation method and air-conditioner thereof | |
| CN210345948U (en) | Air conditioner capable of preventing frosting or keeping heating operation for defrosting for long time | |
| CN203395996U (en) | Air conditioner | |
| CN202002228U (en) | Split-type air conditioner | |
| CN205505203U (en) | Air -conditioner | |
| CN112594956A (en) | Control system for reducing liquid return risk, air conditioner and operation method | |
| KR200300268Y1 (en) | refrigeration system | |
| CN106705306B (en) | The integrated operating system of domestic air conditioner and refrigerator | |
| CN211012012U (en) | Novel air conditioner high pressure reservoir | |
| CN220793408U (en) | Water-cooled central air conditioner |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| PB01 | Publication | ||
| PB01 | Publication | ||
| SE01 | Entry into force of request for substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| GR01 | Patent grant | ||
| GR01 | Patent grant | ||
| TR01 | Transfer of patent right | ||
| TR01 | Transfer of patent right |
Effective date of registration: 20201102 Address after: 266101 Haier Industrial Park, Haier Road, Laoshan District, Shandong, Qingdao, China Patentee after: QINGDAO HAIER AIR CONDITIONER GENERAL Corp.,Ltd. Patentee after: Haier Zhijia Co.,Ltd. Address before: 266101 Haier Industrial Park, Haier Road, Laoshan District, Shandong, Qingdao, China Patentee before: QINGDAO HAIER AIR CONDITIONER GENERAL Corp.,Ltd. |