CN220649205U - Zigzag broken line type finned tube heat exchanger assembly and air conditioner host and equipment platform thereof - Google Patents
Zigzag broken line type finned tube heat exchanger assembly and air conditioner host and equipment platform thereof Download PDFInfo
- Publication number
- CN220649205U CN220649205U CN202322163821.4U CN202322163821U CN220649205U CN 220649205 U CN220649205 U CN 220649205U CN 202322163821 U CN202322163821 U CN 202322163821U CN 220649205 U CN220649205 U CN 220649205U
- Authority
- CN
- China
- Prior art keywords
- heat exchanger
- air
- tube heat
- finned tube
- exchanger assembly
- 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
- 238000004378 air conditioning Methods 0.000 claims abstract description 47
- 238000009423 ventilation Methods 0.000 claims abstract description 19
- 238000005192 partition Methods 0.000 claims abstract description 5
- 239000003507 refrigerant Substances 0.000 claims description 31
- 239000007788 liquid Substances 0.000 claims description 11
- YCKRFDGAMUMZLT-UHFFFAOYSA-N Fluorine atom Chemical compound [F] YCKRFDGAMUMZLT-UHFFFAOYSA-N 0.000 claims description 6
- 229910052731 fluorine Inorganic materials 0.000 claims description 6
- 239000011737 fluorine Substances 0.000 claims description 6
- 238000005452 bending Methods 0.000 claims description 5
- 239000002131 composite material Substances 0.000 claims description 3
- 238000007599 discharging Methods 0.000 claims 1
- 238000010438 heat treatment Methods 0.000 abstract description 9
- 239000003570 air Substances 0.000 description 371
- 238000001704 evaporation Methods 0.000 description 33
- 238000012546 transfer Methods 0.000 description 26
- 230000008020 evaporation Effects 0.000 description 22
- 238000005057 refrigeration Methods 0.000 description 17
- RYGMFSIKBFXOCR-UHFFFAOYSA-N Copper Chemical compound [Cu] RYGMFSIKBFXOCR-UHFFFAOYSA-N 0.000 description 13
- 229910052802 copper Inorganic materials 0.000 description 13
- 239000010949 copper Substances 0.000 description 13
- 238000010521 absorption reaction Methods 0.000 description 12
- 230000006835 compression Effects 0.000 description 11
- 238000007906 compression Methods 0.000 description 11
- 238000013461 design Methods 0.000 description 10
- 230000005494 condensation Effects 0.000 description 8
- 238000009833 condensation Methods 0.000 description 8
- 238000010586 diagram Methods 0.000 description 7
- 239000012080 ambient air Substances 0.000 description 5
- 238000005457 optimization Methods 0.000 description 5
- 230000000694 effects Effects 0.000 description 4
- 230000006872 improvement Effects 0.000 description 4
- 230000006698 induction Effects 0.000 description 4
- 230000008859 change Effects 0.000 description 3
- 238000009792 diffusion process Methods 0.000 description 3
- 238000000034 method Methods 0.000 description 3
- 230000009467 reduction Effects 0.000 description 3
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 3
- 239000011324 bead Substances 0.000 description 2
- 230000009286 beneficial effect Effects 0.000 description 2
- 230000007423 decrease Effects 0.000 description 2
- 230000006866 deterioration Effects 0.000 description 2
- 238000010790 dilution Methods 0.000 description 2
- 239000012895 dilution Substances 0.000 description 2
- 239000006185 dispersion Substances 0.000 description 2
- 239000012530 fluid Substances 0.000 description 2
- 238000012423 maintenance Methods 0.000 description 2
- 230000004048 modification Effects 0.000 description 2
- 238000012986 modification Methods 0.000 description 2
- 230000000149 penetrating effect Effects 0.000 description 2
- 230000008569 process Effects 0.000 description 2
- 230000000630 rising effect Effects 0.000 description 2
- 239000000243 solution Substances 0.000 description 2
- 230000000007 visual effect Effects 0.000 description 2
- 230000001133 acceleration Effects 0.000 description 1
- 230000003321 amplification Effects 0.000 description 1
- 230000005540 biological transmission Effects 0.000 description 1
- 230000015556 catabolic process Effects 0.000 description 1
- 238000006243 chemical reaction Methods 0.000 description 1
- 238000004891 communication Methods 0.000 description 1
- 238000010276 construction Methods 0.000 description 1
- 230000008878 coupling Effects 0.000 description 1
- 238000010168 coupling process Methods 0.000 description 1
- 238000005859 coupling reaction Methods 0.000 description 1
- 230000007547 defect Effects 0.000 description 1
- 238000006731 degradation reaction Methods 0.000 description 1
- 238000006073 displacement reaction Methods 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 230000007613 environmental effect Effects 0.000 description 1
- 238000010304 firing Methods 0.000 description 1
- 238000009413 insulation Methods 0.000 description 1
- 239000010687 lubricating oil Substances 0.000 description 1
- 239000000463 material Substances 0.000 description 1
- 238000003199 nucleic acid amplification method Methods 0.000 description 1
- 230000003068 static effect Effects 0.000 description 1
- 238000004781 supercooling Methods 0.000 description 1
- 238000012932 thermodynamic analysis Methods 0.000 description 1
Landscapes
- Other Air-Conditioning Systems (AREA)
Abstract
The utility model belongs to the technical field of efficient energy-saving air conditioners, and discloses a zigzag folding line type finned tube heat exchanger assembly, an air conditioner host and an equipment platform thereof. The zigzag folding line type finned tube heat exchanger assembly is formed by combining one or two or three of a plurality of flat plate type finned tube heat exchangers and/or a plurality of partition plates and/or V-shaped finned tube heat exchangers; the zigzag folding line type finned tube heat exchanger assembly is zigzag folding line type on a section perpendicular to the long side of the fin. The utility model adopts the zigzag fold line type finned tube heat exchanger assembly, expands the ventilation surface of the finned tube external heat exchanger and the total heat exchange area of the fins which are secondarily unfolded along the ventilation surface, and improves the load intensity and the refrigerating and heating energy efficiency ratio of the air conditioner host. After heat exchange of the air conditioning main machine of each layer of the equipment platform, air is guided by the flow guide plate sheet group in the lateral exhaust section to flow laterally and high-speed to the outer space at the rear side of the air conditioning main machine, so that exhaust air flow is prevented from flowing back to the local equipment platform.
Description
Technical Field
The utility model belongs to the technical field of efficient energy-saving air conditioners, and particularly relates to a zigzag folding line type finned tube heat exchanger assembly, an air conditioner host and an equipment platform thereof.
Background
The basic heat transfer element of the finned tube type heat exchanger is a finned tube, and is formed by combining a base tube and fins. The base pipe is generally a round pipe; the surface structure of the fin is flat fin, intermittent fin, corrugated fin, perforated fin and the like. The fin-tube heat exchanger is widely applied to air conditioner and other equipment, and mainly comprises a plurality of rows of fins and a plurality of rows of copper tubes penetrating through the fins, wherein the inside of the copper tubes is a refrigerant side, the outside of the copper tubes is an air side, and air flows penetrate through fin gaps of the fin-tube heat exchanger so as to exchange heat with the refrigerant inside the copper tubes.
Conventional finned tube heat exchange devices are generally flat plate-like. However, in some applications, it may be desirable to bend the finned tube heat exchange device to separate the heat exchange device into a first heat exchanger portion and a second heat exchanger portion that are at a predetermined angle to each other. In use, the finned tube heat exchanger is placed in the box, and the air flow flows upwards from the lower side of the heat exchanger and exchanges heat with the refrigerant in the heat exchange tubes when passing through the finned tube heat exchanger. The traditional fin type heat exchanger heat exchange technology has the defects of heat exchange dead angles, large difference of the head-on wind speeds of heat exchangers in different areas, uneven heat exchange, large heat exchange area of the heat exchanger and high heat exchanger cost.
The current situation is that the multi-split air conditioner, an air-cooled water machine module and other air conditioning hosts are used for ' air outlet ' and the structural relation between the air conditioning hosts and a building, whether the air conditioning hosts are two-skin ' or the original host, whether an equipment platform is a traditional corridor type structural space is realized, only the space displacement of the air conditioning hosts is implemented, the two air conditioning hosts are not suitable for the structural relation requirement of a building distributed energy system, and the problems of unsmooth air path of the air conditioning hosts, reduced energy efficiency of a refrigerating system, large occupied area of an air inlet and air distribution channel, unreasonable space utilization of the equipment platform, increased occupied area of the host, reduced power density and the like are presented.
The structural problems of the existing air conditioner host and the building distributed energy system are summarized, and mainly include two components:
firstly, the energy density of the air conditioner host equipment platform is low. Through multiple structural optimization and energy efficiency improvement, the calculated power density of the current air conditioner host machine according to the occupied area of the main body is more than 40 kw/square meter, and the power density of the current air conditioner host machine equipment platform is only 11.6 kw/square meter, namely the occupied area of an air conditioner host machine inlet and outlet air duct, a maintenance channel and a ventilation blind area on the platform is more than 2.4 times of the area of the air conditioner host machine; the floor area of the main unit equipment platform of the air conditioner is overlarge at present, which generally reaches more than 1.5% of the total area of the building, and the main unit equipment platform of the air conditioner becomes a prominent problem in the design of heating ventilation and air conditioning of the building.
Secondly, the equipment platform occupies the problem of overlarge transverse width of the outer vertical face of the building. The current air conditioner host and equipment platform have unreasonable wind field structure, low utilization rate of deep space and top space, and overlarge transverse width of building outer elevation occupied by the equipment platform; every 12 equipment floors, the periphery of which are occupied by air inlet and outlet openings of an air conditioner host machine. The width of the outer facade of the building is an important resource next to the building area in the index system of the building, the air conditioner host equipment platform in the high-rise super-high-rise building contends for the width resource of the outer facade of the building, and the transverse width of the outer facade is occupied to be too large, so that the visual communication between the inner space of the same-rise building and the external environment is blocked, and the method also has become an outstanding problem in the design of heating ventilation and air conditioning of the building.
Disclosure of Invention
In order to solve the problems in the prior art, the air conditioner main unit external heat exchanger is uniformly ventilated and exchanges heat under the own environmental pressure; the transverse width of the outer vertical face of the building occupied by the equipment platform is reduced; the utility model provides a zigzag broken line type finned tube heat exchanger assembly, which greatly improves the energy density of an equipment platform and the like;
another object of the present utility model is to provide an air conditioning host of a zigzag-shaped zigzag-type finned tube heat exchanger assembly; the air conditioner host machine comprises a host machine suitable for an air conditioner refrigerating system and also comprises a host machine suitable for an air energy water heater.
Another object of the present utility model is to provide an air conditioning host equipment platform.
In order to solve the technical problems, the technical scheme of the utility model is as follows:
a zigzag folding line type finned tube heat exchanger assembly,
the zigzag folding line type finned tube heat exchanger assembly is formed by combining one or two or three of a plurality of flat plate type finned tube heat exchangers and/or a plurality of partition plates and/or V-shaped finned tube heat exchangers; the zigzag folding line type finned tube heat exchanger assembly is zigzag folding line type on a section perpendicular to the long side of the fin.
Further, the heat exchange tubes of the zigzag folding line type finned tube heat exchanger assembly are parallel to the zigzag edges; the fin group of the fin tube heat exchanger is orthogonally sleeved on the heat exchange tube; the long sides of the fins of the flat plate type fin tube heat exchanger are arranged in the vertical direction or close to the vertical direction.
Further, the V-shaped finned tube heat exchanger consists of 2 flat plate type finned tube heat exchangers, or is formed by bending the flat plate type finned tube heat exchangers, or is formed by bending a plurality of single-row-tube flat plate type finned tubes into a V shape and then assembling the bent single-row-tube flat plate type finned tubes into a composite V-shaped finned tube heat exchanger.
Further, the vertex angle alpha of the V-shaped fin tube heat exchanger is 15-110 degrees.
Preferably, the apex angle alpha of the V-shaped fin tube heat exchanger is 30-90 degrees.
Preferably, the apex angle alpha of the V-shaped fin tube heat exchanger is 30-60 degrees.
Further, the cross section of the zigzag fold line type finned tube heat exchanger assembly perpendicular to the long sides of the fins is of an N type, or the cross section perpendicular to the long sides of the fins is of a W type formed by a V type finned tube heat exchanger, a baffle plate and a flat plate type finned tube heat exchanger; or is a zigzag folded line type formed by a V-shaped finned tube heat exchanger, 2 baffles and 2 flat plate type finned tube heat exchangers.
Further, the included angle gamma between the baffle plate and the flat plate type finned tube heat exchanger is 0.5 alpha;
the included angle epsilon between the baffle plate and the V-shaped finned tube heat exchanger is 0.5 alpha.
Further, one side of the cross section of the zigzag folding line type finned tube heat exchanger assembly vertical to the long sides of the fins is a heat exchanger air inlet surface, and the other side is a heat exchanger air outlet surface; the air outlet surface belongs to the negative pressure cavity area of the external heat exchanger;
the incidence surface of the air inlet flow is provided with each finned tube heat exchanger, and the intersection angle between the air inlet flow and the tip of each fin plate on each finned tube heat exchanger is an obtuse angle beta; the obtuse angle beta is 97.5-145 degrees; the air inlet flow hits the tip of each fin plate at an obtuse angle beta, and is reflected by the fin tip plate to enter the fin gap to flow to the negative pressure cavity of the external heat exchanger;
The flow rate of the air flow entering each fin gap d is equal to the air inlet flow intercepted by the vertical distance delta between the tips of the front fin plate and the rear fin plate of the fin tube heat exchanger on the air inlet section;
delta = d.sin alpha/2, where alpha is the apex angle of the V-type finned tube heat exchanger;
the vertical distance delta value of the tips of the front fin plate and the rear fin plate of the fin tube heat exchanger on the air inlet section is 0.13 d-0.7 d.
An air conditioner main unit provided with the zigzag folding line type finned tube heat exchanger assembly comprises a shell, a finned tube heat exchanger assembly, an air conditioner compressor, a gas-liquid separator and a fan;
the zigzag folding line type finned tube heat exchanger assembly is arranged on the air inlet surface of the air inlet of the shell, and forms a heat exchanger assembly negative pressure cavity communicated with the zigzag folding line type finned tube heat exchanger assembly heat exchange air path with at least part of the shell;
an air outlet is formed in a back plate of the negative pressure cavity of the heat exchanger assembly, and a vertically arranged fan is arranged at the air outlet; the air outlet on the backboard corresponds to an air suction inlet of a vertically arranged fan; the air outlet of the vertically arranged fan is communicated with the air exhaust cavity.
Further, the zigzag folding line type finned tube heat exchanger assembly is a heat exchanger assembly negative pressure cavity air inlet; the exhaust cavity is formed by communicating a vertical exhaust cavity with a lateral exhaust cavity; the air outlet of the fan is communicated with the vertical air exhaust cavity, and the air outlet of the lateral air exhaust cavity is arranged on the same side as the air inlet in the shell and is arranged left and right, so that the air outlet of the air conditioner main machine is arranged.
Further, the air outlet of the lateral air exhaust cavity faces to the short side of the air conditioner main body shell.
Further, the back side of the back plate of the exhaust cavity is provided with a compressor cavity for installing a fluorine circuit assembly comprising an air conditioner compressor, a four-way valve, an expansion valve and an electric box, or,
a compressor cavity for installing a fluorine circuit component comprising an air conditioner compressor, a gas-liquid separator, a four-way valve, an expansion valve and an electric box is arranged on one side outside a negative pressure cavity of a heat exchanger assembly of the shell;
the gas-liquid separator, the air conditioner compressor, the four-way valve, the heat exchanger assembly and the expansion valve are communicated with a refrigerant pipeline of the air conditioner indoor unit to form a refrigerant circulation loop of the air conditioning system.
Further, at least 2 fans are arranged at the air outlet of the negative pressure cavity of the heat exchanger assembly.
Further, the fans are arranged in the same vertical plane.
Further, the fan is an axial flow fan or a centrifugal fan. Preferably, the fan is a backward inclined outer rotor centrifugal fan.
Further, the exhaust cavity is arranged on the side face of the negative pressure cavity side plate of the heat exchanger assembly.
Further, the exhaust cavity is a cavity with a one-way exhaust outlet and is composed of a vertical exhaust cavity and a lateral exhaust cavity which are mutually communicated.
Further, an exhaust section is arranged at the exhaust outlet, and a plurality of flow guide plates are arranged in the exhaust section; the guide plate sheet is vertically arranged and provided with an angle for guiding the exhaust air flow to deviate from the air conditioner main unit.
An air conditioner host machine equipment platform is provided, wherein at least 1 row of air conditioner host machines are transversely arranged in the equipment platform; the equipment platform is provided with an outer vertical surface for ventilation, and an air inlet of the air conditioner host is close to the outer vertical surface; the exhaust outlet of the exhaust cavity is arranged and/or is close to the outer vertical surface.
Further, the exhaust section is arranged adjacent to the equipment platform outer elevation shutter.
Further, an opening structure matched with an exhaust section is arranged on the outer elevation shutter of the equipment platform; the exhaust section is embedded into the opening structure of the shutter.
Further, the opening structure of the equipment platform outer elevation shutter is rectangular, and the long side of the opening structure is parallel to the bottom side or the side edge of the equipment platform.
Further, the air exhaust area on the outer vertical surface corresponds to the air outlet of the air conditioner host, and the air inlet area on the outer vertical surface corresponds to the air inlet of the air conditioner host.
Further, a three-in-one channel for people to carry out maintenance and setting copper pipes and cable bridges of the air conditioning system is formed between the backboard of the air conditioning host and the inner wall surface of the equipment platform.
Compared with the prior art, the utility model has the following beneficial effects:
the utility model adopts the zigzag fold line type finned tube heat exchanger assembly to improve the heat exchange intensity and the heat exchange performance, enlarges the ventilation surface area of the finned tube external heat exchanger and the total heat exchange area of fins which are secondarily unfolded along the ventilation surface, and improves the load intensity and the refrigerating and heating energy efficiency ratio of the air conditioner host.
According to the utility model, as the frame and the flow guide plate of the strip-shaped air outlet of the air conditioner host embedded in the shutter opening structure are not hidden behind the shutter, but are in a straight-face external environment, the strip-shaped air outlet is a part of the outer vertical face of the visible equipment platform, and the frame and the flow guide plate of the air outlet are also decorative, so that the shutter of the outer vertical face of the equipment platform is increased in structural change and color change, and a better decorative visual effect is achieved;
the strip-shaped air outlet of the air conditioner host is arranged on the side edge of the outer elevation shutter and above the water retaining table of the equipment platform, so that the shutter structure design and the site construction are facilitated; the vertical strip air outlet of the air conditioner host embedded into the shutter and the shutter opening structure can be connected without rigid connection, so that the air outlet is suspended in the shutter opening structure or flexibly connected with the shutter opening structure, thereby avoiding the transmission and amplification of the noise of the air conditioner host.
According to the utility model, the air flows after the heat exchange of the air conditioning hosts at each layer are laterally and highly-drifted to the outer space at the rear side of the air conditioning hosts under the constraint and induction of the flow guide plate group in the lateral air exhaust section, the air exhaust flows are separated from the space right in front of the equipment platform, the back flow of the air exhaust flows to the local equipment platform is stopped, and the risk that the air exhaust flows are sucked by the air conditioning hosts of the lower adjacent equipment platform (winter) or by the air conditioning hosts of the upper adjacent equipment platform (summer) after being exhausted from the local equipment platform is stopped.
(1) High-efficiency heat exchange air path structure of air conditioner main machine finned tube heat exchanger assembly is constructed, and energy density of body is improved
The utility model relates to a zigzag fold line type finned tube heat exchanger assembly, wherein a finned tube heat exchanger is arranged in a limited space of an air conditioner main unit in a direction parallel to an air inlet surface of an air inlet of the air conditioner main unit, and is unfolded along the air inlet surface of the finned tube heat exchanger to obtain a large-area ventilating surface of the finned tube heat exchanger assembly, and the ventilating surface of the large-area finned tube heat exchanger assembly is unfolded for the second time to obtain a large-area finned heat transfer surface.
The air flow outside the air conditioner main unit enters the air conditioner main unit at a medium speed of about 4m/S, is decelerated and dispersed in the air conditioner main unit, passes through a finned tube heat exchanger with the characteristics of large total ventilation section and huge total fin heat exchange area S at a low speed of less than 1.6m/S to exchange heat, flows into a negative pressure cavity after heat exchange, is collected to a fan air suction port under the traction of fan negative pressure, is boosted by a fan, and is finally discharged from an air exhaust cavity at a high speed of about 8 m/S.
In the chain flow of medium-speed air intake, dispersion and deceleration of the airflow of the heat exchanger, heat exchange on huge fin heat exchange areas on a huge total ventilation surface, collection and acceleration, fan boosting and high-speed discharge, the airflow takes the fan as a power source, takes a negative pressure cavity as a core, takes a zigzag broken-line type fin tube heat exchanger assembly as a lowest speed area, completes pressurization of a primary fan and static pressure-dynamic pressure conversion of the front and rear of the fan, is efficient and smooth, and builds the air path structure of efficient heat exchange inside the air conditioner host;
according to the vertical arrangement of the centrifugal fans, the straight-face fin tube heat exchanger assembly of the air suction inlet reduces the upward turning local resistance of the air flow before the suction inlet of the traditional multi-split air conditioner, and the throttling effect of the fin planing tool and the fin clearance is combined, so that the ventilation and heat exchange uniformity of the external heat exchanger is improved;
the utility model breaks through the non-uniformity problem of vertical ventilation heat exchange of the traditional multi-split external heat exchanger, the height of the external heat exchanger can break through the traditional design of about 1200mm, the height of the external heat exchanger can be improved to more than 2000mm, and the energy density of the main body of the air conditioner can be improved.
(2) Creating conditions for constructing side-in-side air outlet path structure by matching with outer vertical surface of equipment platform
The utility model has compact structure, and the air inlets of the air outlets of the air conditioner host are arranged on the same side and left and right sides, thus preparing conditions for installing on the equipment platform and arranging the air conditioner host side air outlet structure by matching with the outer elevation of the equipment platform;
according to the utility model, under the design concept that the area of the air inlet of the air conditioner main unit is equal to the area of the air outlet of the air conditioner main unit is approximately equal to 2:1, the air exhaust speed is 2 times that of the air inlet, the air exhaust dynamic pressure head is 4 times that of the air inlet dynamic pressure head, the air exhaust speed and kinetic energy of the air conditioner main unit external heat exchanger are effectively improved, and the range and diffusion dilution effect of the air conditioner main unit air exhaust jet penetrating through the external vertical surface of the equipment platform and entering the environment atmosphere are effectively improved.
Drawings
FIG. 1 is a schematic view of a three-dimensional structure of a fin tube heat exchanger of example 1 with a V-shaped horizontal section;
FIG. 2 is a schematic view showing a three-dimensional structure of a zigzag type fin tube heat exchanger assembly of example 1;
FIG. 3 is a horizontal cross-sectional view of a zigzag-shaped broken-line type finned tube heat exchanger assembly for intercepting an air inlet flow to be decelerated into a fin gap for heat exchange and then discharged into a negative pressure cavity by 'fin planing a fin planing tool in a ladder manner' at a fin gap inlet when an air conditioner main unit of the embodiment 1 operates;
FIG. 4 is a schematic diagram showing the total temperature difference of the condensing temperature and the evaporating temperature of the air conditioning system, which is formed by accumulating the heat transfer temperature difference of the condenser body, the heat transfer temperature difference of the high-temperature low-temperature heat source and the heat transfer temperature difference of the evaporator body 3 when the air conditioning system constructed by the zigzag folding line type finned tube heat exchanger assembly of the embodiment 1 is operated;
FIG. 5 is a schematic diagram of a refrigeration cycle of a pressure enthalpy diagram with increased heating and evaporating pressure resulting from increased heat absorption capacity of refrigerant per unit mass, reduced compression work, increased COP, increased refrigerant circulation capacity of the air conditioning system, and increased heat release capacity of the evaporator heat absorption condenser, resulting from increased heat exchange area of the outer heat exchanger and fins of the heat pump air conditioning system;
FIG. 6 is a three-dimensional schematic diagram of an air conditioner main unit with a lateral exhaust cavity and an exhaust airflow lateral drifting feature, which is provided with a zigzag fold line type finned tube heat exchanger assembly in embodiment 2;
FIG. 7 is a top view of a side-draft air conditioner main unit structure with side-draft air cavities having side-draft air flow side-firing features for a zigzag-shaped zigzag-type finned tube heat exchanger assembly of example 2;
FIG. 8 is a vertical cross-sectional view of the operating airflow of a main air conditioner with a lateral exhaust chamber having the feature of lateral drift of the exhaust airflow, provided with a zigzag-shaped broken-line type finned tube heat exchanger assembly according to embodiment 2;
FIG. 9 is a schematic diagram of an air conditioning system having a zigzag-type finned tube heat exchanger assembly according to embodiment 2;
FIG. 10 is a top plan view of the air flow operation of embodiment 3 with a rear fan wall, side air discharge, and side air flow drifting air conditioner host equipment platform;
FIG. 11 is a schematic diagram showing the distribution of air inlet surfaces on the outer vertical surface of a platform of the air conditioner in summer operation with a rear fan wall, lateral air exhaust and airflow lateral drifting air conditioner host in embodiment 3;
fig. 12 is a schematic diagram showing the vertical hot air flow collection and upward movement of a multi-layer (high-rise) building when the air conditioner host machine with the equipment platform of embodiment 3 is installed with a rear fan wall, laterally exhausted air and laterally blown air.
Detailed Description
For the purposes, technical solutions and advantages of the present application, the technical solutions of the present application will be clearly and completely described below with reference to the drawings of the embodiments of the present application. It will be apparent that the described embodiments are some, but not all, of the embodiments of the present application. All other embodiments, based on the described embodiments, which a person of ordinary skill in the art would obtain without inventive faculty, are within the scope of protection of the present application.
Unless otherwise defined, technical or scientific terms used herein should be given the ordinary meaning as understood by one of ordinary skill in the art to which this application belongs. The terms "first," "second," and the like, as used herein, do not denote any order, quantity, or importance, but rather are used to distinguish one element from another. The word "comprising" or "comprises", and the like, means that elements or items preceding the word are included in the element or item listed after the word and equivalents thereof, but does not exclude other elements or items. The terms "connected" or "connected," and the like, are not limited to physical or mechanical connections, but may include electrical connections, whether direct or indirect.
In the description of the present utility model, it should be understood that the terms "transverse," "longitudinal," "length," "upper," "lower," "left," "right," and the like indicate orientations or positional relationships based on the orientation or positional relationships shown in the drawings, merely to facilitate description of the present utility model and simplify the description, and do not indicate or imply that the devices or elements referred to must have a specific orientation, be configured and operated in a specific orientation, and thus should not be construed as limiting the present utility model.
Definition: the outer facade of the corridor type equipment platform is set to be longitudinal, and the outer facade of the corridor type equipment platform is set to be transverse.
Example 1
1-5, a zigzag-shaped broken-line type finned tube heat exchanger assembly, which is composed of 1 flat-plate type finned tube heat exchanger 37, 1V-shaped finned tube heat exchanger 40, and 1 partition plate 39; the zigzag type fin tube heat exchanger assembly is zigzag type in a section perpendicular to the long sides of the fin plates 110.
The heat exchange tubes 115 of the zigzag-shaped broken-line type finned tube heat exchanger assembly are parallel to the zigzag edges; the fin group of the fin tube heat exchanger is orthogonally sleeved on the heat exchange tube 115; the fin plates 110 of the flat plate type fin tube heat exchanger are disposed in a longitudinal direction or nearly in a longitudinal direction.
The V-shaped finned tube heat exchanger 40 consists of 2 flat plate type finned tube heat exchangers 37, or is formed by bending the flat plate type finned tube heat exchangers 37, or is formed by bending a plurality of single-row tube flat plate type finned tubes into a V shape and then assembling the bent single-row tube flat plate type finned tubes into a composite V-shaped finned tube heat exchanger;
as an alternative embodiment, the V-fin tube heat exchanger 40 has a top angle α of 15 ° to 110 °.
As an alternative embodiment, the V-fin tube heat exchanger 40 has a top angle α of 30 ° to 90 °.
As an alternative embodiment, the V-fin tube heat exchanger 40 has a top angle α of 30 ° to 60 °.
The cross section of the zigzag fold line type finned tube heat exchanger assembly perpendicular to the long sides of the fins is of an N type, or the cross section perpendicular to the long sides of the fins is of a W type formed by a V type finned tube heat exchanger 40, a baffle 39 and a flat plate type finned tube heat exchanger 37; or a V-shaped fin tube heat exchanger 40 with 2 baffles 39 and 2 flat plate fin tube heat exchangers 37.
The angle of the included angle gamma between the partition 39 and the flat plate type fin tube heat exchanger 37 is 0.5α;
the angle of the angle epsilon between the baffle 39 and the V-fin tube heat exchanger 40 was 0.5α.
As shown in fig. 2, one side of the cross section of the zigzag folding line type finned tube heat exchanger assembly vertical to the long sides of the fins is a heat exchanger air inlet surface, and the other side is a heat exchanger air outlet surface; the air outlet surface belongs to the negative pressure cavity area of the external heat exchanger;
The incidence surface of the air inlet flow is each finned tube heat exchanger, and the intersection angle between the air inlet flow and the tip of each fin plate 110 on each finned tube heat exchanger is an obtuse angle beta; the obtuse angle beta is 97.5-145 degrees; the incoming air stream impinges the tips of each fin plate 110 at an obtuse angle β, and is reflected by the fin tip plate 110 into the fin gap to flow to the outer heat exchanger negative pressure cavity 124;
the flow rate of the air flow entering each fin gap d is equal to the air inlet flow intercepted by the vertical distance delta between the tips of the front fin plate and the rear fin plate of the fin tube heat exchanger on the air inlet section;
delta = d.sin alpha/2, wherein alpha is the apex angle alpha of the V-type finned tube heat exchanger;
the vertical distance delta value of the fin tips of the front fin plate 110 and the rear fin plate 110 of the fin tube heat exchanger on the air inlet section is 0.13 d-0.7 d.
As a specific embodiment, the air flow speed of the fin gap is 1/3 of the air inlet speed, and the incidence obtuse angle beta corresponding to the vertex angle alpha of the V-shaped fin tube heat exchanger is 39 degrees and 109.5 degrees.
The core targets of the main machine optimization of the refrigeration (heat pump) air conditioner under different application scenes are still that the condensation pressure is reduced and the evaporation pressure is increased: the refrigeration condensing pressure is reduced, so that the compression work of the compressor can be directly reduced; and the heating evaporation pressure (evaporation temperature) of the heat pump is increased, namely the circulation quantity of the refrigerant is increased, the heat absorption capacity of the evaporator is increased, the heat release capacity of the condenser is increased, the compression ratio is reduced, and the exhaust temperature of the compressor is reduced.
The present embodiment innovatively takes the evaporation pressure (evaporation temperature) as the first factor of the refrigerating and air-conditioning system, because the evaporation pressure determines the density of the low-pressure refrigerant gas sucked by the compressor and the compression ratio of the compressor, if the evaporation pressure of the heat exchanger (evaporator) outside the heat pump air-conditioning main unit is increased from 5 kg to 6 kg in winter, the system refrigerant circulation amount, the heat absorption amount of the evaporator, the heat release amount of the condenser must be increased by 20% simultaneously, and the compression ratio of the compressor, the exhaust temperature of the compressor should also fall.
The embodiment innovatively analyzes the relation Q=KxSx% delta t between the heat exchange quantity Q and the total heat transfer coefficient K, the heat exchange area S and the heat transfer temperature difference delta t between the refrigerant and the air of the finned tube heat exchanger such as the air conditioner evaporator condenser, and provides the technical judgment of increasing the total heat transfer area S of the finned tube heat exchanger for improving the evaporation pressure of the current air conditioner host, reducing the condensation pressure, improving the heat exchange capacity Q of the external heat exchanger of the air conditioner host and the COP of the refrigeration air conditioner system.
From the existing external heat exchanger of the air conditioner, in the heat exchange quantity Q=KxSxdelta t of the heat exchanger, the route of greatly increasing the heat exchange quantity Q by enlarging the total heat transfer coefficient K and the heat transfer temperature difference delta t of the heat exchanger body is not effective any more. Because the corrugated fins, the slotted fins and the internal thread copper pipes are widely applied to the existing evaporator condenser of the refrigeration air-conditioning system, the total heat transfer coefficient K of the external heat exchanger of the air-conditioning host machine is close to the peak value, and the marginal effect of improving the K value by optimizing the fin structure, the copper pipe structure and the air flow interrelationship of the fin copper pipes is greatly reduced. And the heat exchange quantity Q is expected to be increased by expanding the heat transfer temperature difference delta t of the condenser body of the condenser under the determined low-temperature heat source and high-temperature heat source scenes, namely under the specific determined conditions of the thermophysical parameters such as the temperature, the humidity and the like of the high-temperature medium low-temperature medium where the condenser evaporator operates, and the heat exchange quantity Q is not effective any more. Because the delta t between the low-temperature medium (such as indoor low-temperature air in summer) between the evaporator fins and the refrigerating fluid in the copper pipe is enlarged, the evaporation temperature and the evaporation pressure are necessarily reduced; if delta t between high-temperature high-pressure refrigerant gas in the copper pipe of the condenser and high-temperature medium (such as summer high-temperature ambient air) between the fins is enlarged, the condensation pressure and the condensation temperature are necessarily raised. Therefore, the scheme of expanding the heat transfer temperature difference delta t of the heat exchanger bodies such as the evaporator condenser and the like to improve the heat exchange quantity Q of the heat exchanger just damages the refrigerant circulation quantity, the heat absorption capacity, the heat release capacity and the COP of the air conditioning system of the whole refrigeration system.
Therefore, under the conditions that the materials and the structures of the heat exchanger are optimized deeply and the target value of the COP of the system is continuously improved, the potential of increasing K and delta t to increase Q is exhausted, and how to improve the heat exchange capacity of the heat exchanger becomes a great technical difficulty.
The embodiment not only increases the heat exchange capacity of the heat exchanger but also improves the performance of the refrigeration and air-conditioning system by enlarging the heat exchange area of the evaporator/condenser. The heat exchange area is enlarged, the heat exchange temperature difference is reduced, and the heat exchange device is not only an objective requirement for iterative upgrade of the heat exchanger, but also a core requirement for iterative upgrade of a large refrigerating air conditioner system constructed by the heat exchanger.
As shown in fig. 4, the difference between the condensing temperature and the evaporating temperature (T 2 -t 2 ) Is the fundamental factor for determining the COP of the core index of the refrigeration and air-conditioning system, this (T 2 -t 2 ) High then the COP is low, this (T 2 -t 2 ) The COP is high when the COP is low, and the difference between the COP of the refrigeration and air-conditioning system and the evaporating temperature of the condensing temperature (T 2 -t 2 ) Inverse correlation; and the difference between the condensing temperature and the evaporating temperature (T 2 -t 2 ) And the heat transfer temperature difference (T) 2 -T 1 ) Low temperature heat source temperature difference (T) 1 -t 1 ) Heat transfer temperature difference (t) of evaporator body 1 -t 2 ) These 3 differences are accumulated. Therefore, the temperature difference of the low temperature heat source at the high temperature heat source (T 1 -t 1 ) As objective condition that can not be changed, the utility model innovatively reduces the heat transfer temperature difference (T) 2 -T 1 ) Heat transfer temperature difference (t) of evaporator body 1 -t 2 ) Is to reduce the difference (T) 2 -t 2 ) The only paths of the system are the only paths of reducing the condensation pressure (condensation temperature), increasing the evaporation temperature (evaporation pressure), increasing the circulation quantity of the refrigerant, increasing the heat absorption quantity of the evaporator, the heat release quantity of the condenser and increasing the COP of the refrigerating and air conditioning system.
As shown in fig. 5, the utility model reduces the heat transfer temperature difference of the body of the evaporator condenser by enlarging the total heat transfer area S of the fins of the finned tube heat exchanger, improves the evaporating pressure and reduces the condensing pressure, thereby achieving the aims of improving the circulation quantity of the refrigerant, the heat absorption quantity of the evaporator, the heat release quantity of the condenser and the COP of the refrigerating system. The technical effect of enlarging the heat exchange area of the total fins of the external heat exchanger is particularly reflected in the improvement of the evaporation temperature and the evaporation pressure of the evaporator.
The evaporating pressure is the first factor of the heat pump system, and the influence on the performance of the heat pump system of the refrigerating system is shown in figure 2 (the ordinate is condensing pressure, the abscissa is enthalpy value, 1-2-3-4 in the figure are the original circulation paths, 1-2-3 ， -4 ， For the circulation path of the present utility model):
(1) Increased evaporation pressure (P) 1 →P 1 ， ) Directly brings the increase of the heat absorption capacity of the refrigerant in unit mass of the refrigeration system (h 4 ， －h 4 ) Compressor compression work reduction (h) 4 ， －h 4 ) The energy efficiency ratio is improved;
(2) Increased evaporation pressure (P) 1 →P 1 ， ) And also directly brings about an increase in the refrigerant circulation amount of the fixed-frequency heat pump system (P 1 ， /P 1 -1) x 100% with an increase in evaporator heat absorption power and condenser heating power (P) 1 ， /P 1 －1)×100％；
(3) The increase in the evaporating pressure also directly leads to a reduction in the compression ratio and a reduction in the compressor discharge temperature, effectively suppressing the deterioration of the lubricating oil and the deterioration of the compressor motor insulation performance.
When the finned tube heat exchanger assembly of the utility model operates, the microscopic process that air flows in and out of the fin gaps and flows at low speed in the fin gaps is the central link of the finned tube heat exchanger assembly in and out of the wind field.
As shown in FIG. 3, at the section E-E of the air flow inlet of the zigzag folding-line type finned tube heat exchanger assembly, medium-speed air flow about 4m/s which is introduced from the outer vertical surface of the equipment platform is pushed to the section F-F of the fin gap inlet in a uniform laminar flow mode, the air inlet air flow line at the section F-F forms an obtuse angle beta with the fin at the back side of the gap, and the fin at the back side of the gap is used as a planer tool to 'plane' a piece of air flow from air flow of the air inlet main body to be plugged into the fin gap; the main body air inlet airflow which is "shaved" is intercepted by the blade tip of the "fin shaver" at the F-F position, and the blade tip of the "fin shaver" at the back side of the gap is impacted by an obtuse angle beta, and is diffused and decelerated in the gap of the fins after being reflected by the fins at the front side of the gap; the air flow which is planed by the fin planing tool and is subjected to collision diffusion deceleration is pulled by negative pressure of the negative pressure cavity at about 1.5m/s, and flows out of the fin channel against the resistance of the fin gap channel; the low-speed air flow reaching the G-G section of the fin gap outlet is accelerated again to a medium-speed air flow of about 4m/s under the negative pressure pulling of the negative pressure cavity, and is collected and discharged at the H-H section.
Based on the thermodynamic analysis, the utility model aims to enlarge the total heat transfer area S of the fins of the fin tube external heat exchanger in three factors K, S and delta t which form the external heat exchanger Q of the air conditioner host.
The effort of expanding the total heat transfer area S of the fins of the fin tube external heat exchanger is beneficial to improving the air path structure of the heat exchanger of the air conditioner host, improving the running efficiency of the air path and reducing the power consumption of a fan. No matter what air duct structure the air flow of the external heat exchanger of the air conditioner main unit flows in, no matter the resistance along the air duct flow path or the local resistance caused by the air duct reducing and turning is proportional to the square of the air duct air flow speed, namely, the delta P=zeta v 2 The complexity of the air duct structure and the complexity of the air flow thermophysical characteristics both lead to the complexity of the proportionality coefficient zeta and are reflected in the complexity of zeta without changing the delta P and the delta v 2 The basic relationship of (1), i.e. the equation Δp=ζv 2 Expressed delta P-v 2 Relationship. In this embodiment, while "enlarging the total area S of fins of the heat exchanger to increase evaporation pressure, decrease condensation pressure, and increase heat exchange capacity", enlarging the total area S of fins of the heat exchanger also increases the total ventilation area of the fin outer tube heat exchanger and decreases the ventilation speed between fins under a determined air volume of the heat exchanger outside the air conditioner main unit, thereby passing Δp=ζv 2 The mathematical relationship of the air flow speed and speed distribution is controlled to reduce the local resistance delta P of the air flow along the way, reduce the air path resistance and reduce the power consumption of the fan.
Example 2
As shown in fig. 6 to 9, an air conditioner main unit provided with a zigzag-shaped broken-line type finned tube heat exchanger assembly comprises a shell 1, a finned tube heat exchanger assembly 2, an air conditioner compressor 121, a gas-liquid separator 126 and a fan 38;
the zigzag folding line type finned tube heat exchanger assembly is arranged on the air inlet surface of the air inlet 125 of the shell, and forms a heat exchanger assembly negative pressure cavity 124 communicated with a heat exchange air path of the zigzag folding line type finned tube heat exchanger assembly with at least part of the shell;
an air outlet is arranged on the back plate 142 of the negative pressure cavity of the heat exchanger assembly, and a vertically arranged fan 38 is arranged at the air outlet; an air outlet on the negative pressure cavity backboard corresponds to an air suction inlet of the vertically arranged fan; the air outlet of the vertically arranged fan 38 communicates with the air discharge chamber 33.
The zigzag fold line type finned tube heat exchanger assembly is an air inlet of a negative pressure cavity 124 of the heat exchanger assembly; the exhaust outlet 331 of the exhaust chamber 33 is arranged on the same side as the air inlet 125 in the housing, and is arranged left and right. The air outlet 331 of the air discharge chamber 33 faces the short side of the air conditioner main body case.
The rear side of the back plate of the discharge chamber 33 is provided with a compressor chamber 332 for mounting a fluorine circuit assembly including an air conditioner compressor 121, a four-way valve, an expansion valve and an electric box,
2 fans are arranged at the air outlet of the negative pressure cavity 124 of the heat exchanger assembly; the fans 38 are disposed in the same vertical plane. Fan 38 is a retroverted outer rotor centrifugal fan.
As an alternative embodiment, the air exhaust chamber 33 is composed of a vertical air exhaust chamber and a lateral air exhaust chamber which are communicated with each other; wherein, the lateral exhaust cavity is arranged left and right with the bottom plate of the negative pressure cavity of the heat exchanger assembly.
The finned tube heat exchanger assembly is an air inlet of a negative pressure cavity 124 of the heat exchanger assembly; the exhaust outlet 331 of the exhaust chamber 33 is arranged on the same side as the air inlet 125 in the housing, and is arranged left and right. The air outlet 331 of the air exhaust chamber faces the short side of the air conditioner main body case.
An exhaust section 35 is arranged at the exhaust outlet, and a plurality of flow guide plates 34 are arranged in the exhaust section 35; a plurality of small-angle lateral flow guide plates are arranged in the exhaust section.
The gas-liquid separator, the air conditioner compressor, the four-way valve, the heat exchanger assembly, the expansion valve and the refrigerant pipeline of the air conditioner indoor unit are sequentially communicated to form a refrigerant circulation loop of the air conditioner system.
When the embodiment operates, the exhaust air flows are emitted to the rear of the air conditioner host under the constraint and induction of the small-angle lateral flow guide plates, and the exhaust air flows fly away from the space right in front of the equipment platform where the air conditioner host is positioned, so that the possibility of backflow of the air inlet of the air conditioner host is avoided.
Aiming at the problems that the energy density of the existing air conditioner host equipment platform is too low, the width resources of the outer vertical face of a building are occupied too much and the like, the embodiment innovates and makes optimization of the performance of the air conditioner host, optimization of the structure of the air inlet and outlet field of the building equipment platform and energy coupling characteristics and improvement of the air conditioner host and the equipment platform from the thermodynamic fluid mechanics.
The core objective of the design optimization of the refrigeration (heat pump) air conditioner host in this embodiment is still "reduce condensing pressure, raise evaporating pressure": the compression work of the compressor can be directly reduced because the refrigeration condensing pressure is reduced; and the heating evaporation pressure (evaporation temperature) of the heat pump is increased, namely the circulation quantity of the refrigerant is increased, the heat absorption capacity of the evaporator is increased, the heat release capacity of the condenser is increased, the compression ratio is reduced, and the exhaust temperature of the compressor is reduced. Because the evaporation pressure determines the density of the low-pressure refrigerant gas sucked by the compressor and the compression ratio of the compressor, if the evaporation pressure of the heat exchanger (evaporator) outside the heat pump air conditioner main unit is increased from 5 kg to 6 kg in winter, the system refrigerant circulation amount, the evaporator heat absorption amount and the condenser heat release amount are necessarily increased by 20% synchronously, and the compression ratio of the compressor and the exhaust temperature of the compressor should also fall.
The air conditioner host machine of the embodiment innovates the design of the air conditioner host machine from the aspects of expanding the total area of the ventilation section and the total area of fins of the outer heat exchanger of the air conditioner host machine, reducing the heat transfer temperature difference of the outer heat exchanger body, controlling the air flow speed and the flow resistance of the fin gaps of the outer heat exchanger, and the like:
(1) innovative host structure design
In the embodiment, a finned tube heat exchanger assembly is constructed in the air conditioner host along the direction parallel to the air inlet surface of the air inlet, and is arranged close to the air outlet of the air inlet of the air conditioner host, so that the main section of the air exhaust channel of the air inlet channel of the finned tube heat exchanger assembly is brought into the air conditioner host;
in the limited space of the air conditioner host, the zigzag fold line type finned tube heat exchanger assembly is arranged in parallel to the direction of the air inlet surface of the air conditioner host air inlet, the large-area heat exchanger assembly ventilation surface is obtained by unfolding the zigzag fold line type finned tube heat exchanger assembly along the air inlet surface of the finned tube heat exchanger, and the large-area fin heat transfer surface is obtained by unfolding the large-area heat exchanger assembly ventilation surface for the second time, so that the total fin heat exchange area S of the air conditioner host finned tube heat exchanger assembly is effectively enlarged, the heat transfer temperature difference delta t of the heat exchanger body is reduced, the evaporating pressure is increased, the condensing pressure is reduced, and the refrigerating capacity Q and the energy efficiency ratio COP of the refrigerating and air conditioning system are improved.
At least 1 heat exchanger assembly negative pressure cavity is arranged in the implementation, and the negative pressure cavity is formed by combining a bottom plate, a side plate, a back plate, a fin tube external heat exchanger and a top plate; the back plate is arranged opposite to the transverse continuous fin tube heat exchanger assembly, a negative pressure cavity air outlet of the heat exchanger assembly is arranged on the back plate, a fan is arranged at the air outlet, a backward inclined outer rotor centrifugal fan is preferred, and an air suction inlet of the backward inclined outer rotor centrifugal fan faces the fin tube heat exchanger assembly; the finned tube heat exchanger assembly is a negative pressure cavity air inlet; an exhaust cavity is arranged below the negative pressure cavity bottom plate, an exhaust outlet of the exhaust cavity is arranged on the same side as an air inlet of the air conditioner main unit, and the air inlet of the exhaust cavity is communicated with a fan air outlet of the negative pressure cavity of the continuous heat exchanger assembly; the rear side of the back plate of the exhaust cavity is provided with a compressor cavity, and fluorine circuit components such as an air conditioner host compressor, a four-way valve, an expansion valve, an electric box and the like are arranged.
(2) Innovative design of air conditioner main unit external heat exchanger air inlet and outlet field
In the embodiment, focusing on lifting the height of the finned tube heat exchanger assembly of the air conditioner main unit, a vertical exhaust cavity is arranged at the rear side of the finned tube heat exchanger assembly, and a lateral exhaust cavity is arranged at the outer side of a side plate of the finned tube heat exchanger assembly to vacate space; the air outlet of the lateral air exhaust cavity is arranged at the same side as the air inlet of the air inlet channel, and is arranged left and right, and the area of the air outlet is obviously smaller than that of the air inlet;
In the embodiment, the air inlet and outlet field of the finned tube heat exchanger assembly is established through the operation of a fan: the air in the negative pressure cavity of the vertical centrifugal fan suction heat exchanger assembly generates negative pressure in the cavity, ambient air is pulled to enter the air conditioner main unit from the air inlet of the air conditioner main unit at medium speed, the air inlet flow is dispersed and decelerated through the multi-fin planing tool to plane the main body air inlet flow in a gradient manner, the heat exchange is completed by low-speed flow through fin gaps, the air enters the negative pressure cavity of the heat exchanger assembly, the air enters the centrifugal fan air inlet with the lowest accelerating inflow pressure in a converging manner, the air is boosted by a fan, and the air is discharged at high speed outwards after passing through the vertical air exhaust cavity and the lateral air exhaust cavity.
When the air conditioner main unit of the embodiment operates, the microscopic process that the air flow enters and exits the fin gaps and flows at low speed in the fin gaps is the central link of the fin tube heat exchanger assembly entering and exiting the wind field.
(3) Design innovation of refrigeration circuit
The air conditioner main unit of the embodiment is characterized in that a compressor cavity is arranged on the outer side of a back plate of an exhaust cavity, and circuit components such as a compressor, a four-way valve, an expansion valve, a gas-liquid separator and the like, and a power cable signal wire electric box and the like are arranged; the components of the refrigeration loop element, the external heat exchanger, the refrigerant connecting pipe, the indoor unit heat exchanger and the like form a refrigeration air-conditioning circulation loop according to the sequence of a compressor, a four-way valve, a condenser, an expansion valve, an evaporator, a four-way valve, a gas-liquid separator and a compressor; the compressor is used as refrigeration cycle loop power, a high-low pressure state of a refrigerant is respectively established in a condenser evaporator pipeline, the refrigerant is driven to circularly flow and repeatedly change phase in the refrigeration cycle loop to realize 'heat transfer', namely, heat of low-temperature ambient air flowing through gaps of fins is absorbed through a huge fin heat absorption area S formed by evaporating and absorbing heat of refrigerant liquid in the evaporator pipeline and then rising and connecting a copper pipe, heat is released through high-temperature high-pressure refrigerant gas condensed and released in the condenser pipeline and then released to high-temperature ambient air flowing among the fins through a huge fin heat release area S formed by rising and connecting the copper pipe, and heat transfer from a low-temperature environment where an air conditioner evaporator is located to a high-temperature environment where the condenser is located is realized.
When the air conditioner main unit of the embodiment operates, the centrifugal fan of the negative pressure cavity of the heat exchanger assembly operates to pump and exhaust air in the negative pressure cavity of the heat exchanger assembly corresponding to the air suction port of the centrifugal fan, negative pressure is generated in the cavity, and air outside the outer heat exchanger is pulled to enter the air conditioner main unit at medium speed; after outside air enters the air conditioner main unit, the main body air inlet flow is planed in a ladder manner by a plurality of fin planing cutters to realize the dispersion and deceleration of the air inlet flow, and the air flows through the fin gaps of the heat exchanger with large total ventilation section and huge fin total area at low speed, so that the heat exchange between the ambient air and the refrigerant in the copper pipe of the heat exchanger is realized; air entering the negative pressure cavity after heat exchange is collected and accelerated to flow into a fan air suction port with the lowest pressure, and is boosted by the centrifugal fan to pass through the vertical air exhaust cavity and the lateral air exhaust cavity to be discharged outwards at high speed.
Example 3
As shown in fig. 10-12, an air conditioner host equipment platform is provided, in which 1 row of air conditioner hosts of embodiment 2 are arranged in the transverse direction; the compressor cavity is arranged at the rear, the vertical air outlet is communicated with a lateral air exhaust section 35, a lateral flow guide plate 34 is arranged in the lateral air exhaust section 35, and the flow guide plate 34 points to the side which is back to the air inlet of the air conditioner host computer at a small angle; the deflector sheet 34 is vertically disposed and is provided with an angle that directs the exhaust air flow away from the air conditioning main unit.
According to the embodiment, a shutter is arranged on the outer vertical face of a platform of the air conditioner host machine equipment in a side-to-side exhaust airflow side-to-side drifting mode of a rear fan wall, and a vertical strip-shaped opening capable of freely accommodating a side-to-side exhaust section of the air conditioner host machine is reserved on the shutter close to the side wall; when the air conditioner host is installed, the lateral exhaust section of the air conditioner host is embedded into a vertical strip-shaped opening reserved in the shutter;
when the air conditioner host equipment platform runs, the positive pressure air exhaust cavity of the air conditioner host discharges air after heat exchange into the lateral air exhaust section at high speed, the air exhaust air flows from the horizontal direction to the lateral air exhaust section under the constraint and induction of the flow guide plate group, the air exhaust air flows are separated from the space right in front of the equipment platform, the air exhaust air flows are stopped from flowing back to the local equipment platform, and the risk that the air exhaust air is sucked by a lower adjacent equipment platform (winter) or by an upper adjacent equipment platform (summer) after being discharged from the equipment platform is stopped; seen from the vertical direction, the air-conditioning main machine exhaust air flow of a plurality of layers of equipment platforms of the building is emitted laterally at a small angle in the horizontal plane, then is gathered in the vertical direction of the outer space of the air-conditioning main machine, hot air flow moves upwards in summer, cold air flow moves downwards in winter, and is separated from the vertical space of the equipment platforms, and is diffused and diluted away from the equipment platforms.
When the air conditioner main machine external heat exchanger on the equipment platforms of a plurality of floors in winter (summer) ventilates the environment, the external elevation of the equipment platform has the problems of air conditioner main machine performance degradation caused by the attachment of cold (hot) air of the external elevation of the equipment platform because the external elevation of the equipment platform has small-area air exhaust area, positive pressure, high-speed external air exhaust and large-area air inlet area and micro-negative pressure, low-speed suction of the environment air, and the phenomena of diffusion dilution of the external air exhaust in the atmosphere and partial air exhaust backflow of the external elevation occur:
in winter, cold air discharged by the outer heat exchanger of the air conditioner of each layer of equipment platform is diffused and diluted in front of the outer vertical surface of the outer heat exchanger and partially flows back, the whole cold air discharged by the existing multi-layer equipment platform moves downwards and converges in a vertical direction, the cold air is connected end to end, beads are connected in a chain, the more the strings are, the outer vertical surface of the equipment platform is covered, so that the air conditioner host of the lower layer of equipment platform sucks the cold air discharged by the air conditioner host of the upper layer of equipment platform, the evaporation temperature is reduced, the circulation quantity of the refrigerant is reduced, and the heating performance of the air conditioner host is deteriorated;
in summer, hot air discharged by the outer heat exchanger of the air conditioner of each layer of equipment platform is diffused and diluted in front of the outer vertical surface of the outer heat exchanger and partially flows back, the whole hot air discharged by the existing multi-layer equipment platform moves upwards and converges in a vertical direction, the hot air is connected end to end, beads are connected in a chain, the more the strings are, the outer vertical surface of the equipment platform is covered, so that the air conditioner host of the upper layer of equipment platform sucks the hot air discharged by the air conditioner host of the lower layer of equipment platform, the condensation temperature is raised, the supercooling degree of condensate is reduced, and the refrigerating performance of the air conditioner is deteriorated;
In this embodiment, under the constraint and induction of the flow guide plate group in the lateral exhaust section, the air after heat exchange of the air conditioning main machine in each layer flows to the outside space at the rear side of the air conditioning main machine at a high speed in a lateral direction, and the exhaust air flow is separated from the space right in front of the equipment platform, so that the exhaust air flow is stopped from flowing back to the local equipment platform, and the risk that the exhaust air flow is sucked by the lower adjacent equipment platform (winter) or by the upper adjacent equipment platform (summer) after being exhausted from the local equipment platform is stopped.
It is to be understood that the above examples of the present utility model are provided by way of illustration only and not by way of limitation of the embodiments of the present utility model. Other variations or modifications of the above teachings will be apparent to those of ordinary skill in the art. It is not necessary here nor is it exhaustive of all embodiments. Any modification, equivalent replacement, improvement, etc. which come within the spirit and principles of the utility model are desired to be protected by the following claims.
Claims (19)
1. A zigzag folding line type finned tube heat exchanger assembly is characterized in that,
the zigzag folding line type finned tube heat exchanger assembly is formed by combining one or two or three of a plurality of flat plate type finned tube heat exchangers and/or a plurality of partition plates and/or V-shaped finned tube heat exchangers; the zigzag folding line type finned tube heat exchanger assembly is zigzag folding line type on a section perpendicular to the long side of the fin.
2. The zigzag type finned tube heat exchanger assembly according to claim 1, wherein,
the heat exchange tubes of the zigzag folding line type finned tube heat exchanger assembly are parallel to the zigzag edges; the fin group of the fin tube heat exchanger is orthogonally sleeved on the heat exchange tube; the fin long sides of the fin tube heat exchanger are arranged in the vertical direction or close to the vertical direction.
3. The zigzag type finned tube heat exchanger assembly as claimed in claim 1, wherein the V-shaped finned tube heat exchanger is composed of 2 flat plate type finned tube heat exchangers, or is formed by bending a plurality of flat plate type finned tubes with single row of tubes into a V-shape and then assembling the V-shaped finned tube heat exchangers into a composite V-shaped finned tube heat exchanger.
4. A zigzag type finned tube heat exchanger assembly according to claim 3, wherein the V-shaped finned tube heat exchanger has a top angle α of 15 ° to 110 °.
5. The zigzag type finned tube heat exchanger assembly according to claim 1, wherein,
the cross section of the zigzag fold line type finned tube heat exchanger assembly perpendicular to the long sides of the fins is of an N type, or the cross section perpendicular to the long sides of the fins is of a W type formed by a V type finned tube heat exchanger, a baffle plate and a flat type finned tube heat exchanger; or a zigzag folded line type is formed by the V-shaped finned tube heat exchanger, 2 baffle plates and 2 flat plate type finned tube heat exchangers.
6. The zigzag type finned tube heat exchanger assembly according to claim 1, wherein,
the included angle gamma between the baffle plate and the flat plate type finned tube heat exchanger is 0.5alpha;
the included angle epsilon between the baffle plate and the V-shaped finned tube heat exchanger is 0.5 alpha.
7. The zigzag type finned tube heat exchanger assembly according to claim 1, wherein,
one side of the cross section of the zigzag fold line type finned tube heat exchanger assembly vertical to the long sides of the fins is a heat exchanger air inlet surface, and the other side is a heat exchanger air outlet surface; the air outlet surface belongs to the negative pressure cavity area of the external heat exchanger;
the incidence surface of the air inlet flow is provided with each finned tube heat exchanger, and the intersection angle between the air inlet flow and the tip of each fin plate on each finned tube heat exchanger is an obtuse angle beta; the obtuse angle beta is 97.5-145 degrees; the air inlet flow hits the tip of each fin plate at an obtuse angle beta, and is reflected by the fin tip plate to enter the fin gap to flow to the negative pressure cavity of the external heat exchanger;
the flow rate of the air flow entering each fin gap d is equal to the air inlet flow intercepted by the vertical distance delta between the tips of the front fin plate and the rear fin plate of the fin tube heat exchanger on the air inlet section;
delta = d.sin alpha/2, where alpha is the apex angle of the V-type finned tube heat exchanger;
The vertical distance delta value of the tips of the front fin plate and the rear fin plate of the fin tube heat exchanger on the air inlet section is 0.13 d-0.7 d.
8. An air conditioner main unit provided with the zigzag-shaped broken-line type finned tube heat exchanger assembly as set forth in any one of claims 1 to 7, characterized in that,
comprises a shell, a finned tube heat exchanger assembly, an air conditioner compressor, a gas-liquid separator and a fan;
the zigzag folding line type finned tube heat exchanger assembly is arranged at an air inlet of the shell and is communicated with a heat exchange air path of the zigzag folding line type finned tube heat exchanger assembly through a heat exchanger assembly negative pressure cavity formed by at least part of the shell;
an air outlet is formed in a back plate of the negative pressure cavity of the heat exchanger assembly, and a vertically arranged fan is arranged at the air outlet; the air outlet on the backboard corresponds to an air suction inlet of a vertically arranged fan; the air outlet of the vertically arranged fan is communicated with the air exhaust cavity.
9. The air conditioning main unit of the zigzag-shaped folding-line type finned tube heat exchanger assembly according to claim 8, wherein the air outlet of the air exhaust cavity is arranged on the same side as the air inlet in the shell and is arranged left and right.
10. The air conditioning main unit of the zigzag-shaped folding-line-type finned tube heat exchanger assembly according to claim 9, wherein the air outlet of the air discharging chamber faces the short side of the air conditioning main unit casing.
11. The air conditioning main unit of the zigzag-type finned tube heat exchanger assembly according to claim 8, wherein the rear side of the back plate of the air discharge chamber is provided with a compressor chamber for mounting a fluorine circuit assembly comprising an air conditioner compressor, a four-way valve, an expansion valve and an electric box, or,
a compressor cavity for installing a fluorine circuit component comprising an air conditioner compressor, a gas-liquid separator, a four-way valve, an expansion valve and an electric box is arranged on one side outside a negative pressure cavity of a heat exchanger assembly of the shell;
the gas-liquid separator, the air conditioner compressor, the four-way valve, the heat exchanger assembly and the expansion valve are communicated with a refrigerant pipeline of the air conditioner indoor unit to form a refrigerant circulation loop of the air conditioning system.
12. The air conditioning main unit of the zigzag-shaped folding-line type finned tube heat exchanger assembly according to claim 8, wherein at least 2 fans are installed at an air outlet of a negative pressure cavity of the heat exchanger assembly.
13. The air conditioning main unit of the zigzag-shaped folding-line type finned tube heat exchanger assembly according to claim 12, wherein the fans are arranged in the same vertical plane.
14. The air conditioner main unit of the zigzag folding-line type finned tube heat exchanger assembly according to claim 8, wherein the air exhaust cavity is a cavity with a one-way air outlet and consists of a vertical air exhaust cavity and a lateral air exhaust cavity which are mutually communicated; the lateral exhaust cavity is arranged on the outer side of the side plate of the negative pressure cavity of the heat exchanger assembly.
15. The main unit of the air conditioner of the zigzag type finned tube heat exchanger assembly according to claim 14, wherein an exhaust section is arranged at the exhaust port, and a plurality of deflector sheets are arranged in the exhaust section; the guide plate sheet is vertically arranged and provided with an angle for guiding the exhaust air flow to deviate from the air conditioner main unit.
16. An air conditioner host machine equipment platform, which is characterized in that at least 1 row of air conditioner host machines according to any one of claims 8-15 are transversely arranged in the equipment platform; the equipment platform is provided with an outer vertical surface for ventilation, and an air inlet of the air conditioner host is close to the outer vertical surface; the exhaust outlet of the exhaust cavity is arranged and/or is close to the outer vertical surface.
17. The air conditioner host device platform of claim 16, wherein said air discharge section is disposed adjacent to the device platform facade blind.
18. The air conditioner host device platform of claim 16, wherein the outer-face shutter of the device platform is provided with an opening structure matched with the exhaust section; the exhaust section is embedded into the opening structure of the shutter.
19. The air conditioner mainframe equipment platform of claim 17, wherein the open configuration of the louver is rectangular with the long sides parallel to the equipment platform sides.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202322163821.4U CN220649205U (en) | 2023-08-11 | 2023-08-11 | Zigzag broken line type finned tube heat exchanger assembly and air conditioner host and equipment platform thereof |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202322163821.4U CN220649205U (en) | 2023-08-11 | 2023-08-11 | Zigzag broken line type finned tube heat exchanger assembly and air conditioner host and equipment platform thereof |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN220649205U true CN220649205U (en) | 2024-03-22 |
Family
ID=90294470
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202322163821.4U Active CN220649205U (en) | 2023-08-11 | 2023-08-11 | Zigzag broken line type finned tube heat exchanger assembly and air conditioner host and equipment platform thereof |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN220649205U (en) |
-
2023
- 2023-08-11 CN CN202322163821.4U patent/CN220649205U/en active Active
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN117190302A (en) | Negative pressure cavity exhaust cavity complementary design heavy load air conditioner host and equipment platform thereof | |
| CN220649205U (en) | Zigzag broken line type finned tube heat exchanger assembly and air conditioner host and equipment platform thereof | |
| CN116858011A (en) | Zigzag broken line type finned tube heat exchanger assembly and air conditioner host and equipment platform thereof | |
| CN220556201U (en) | Air conditioner host computer of fan vertical arrangement and equipment platform thereof | |
| CN219889664U (en) | Outer corridor type equipment platform adopting zigzag type finned tube heat exchanger air conditioner host | |
| CN219841604U (en) | Fin tube heat exchanger assembly, air conditioner host and air conditioner system thereof | |
| CN220552024U (en) | Main unit fusion body of fan rear-mounted double-air-duct double-refrigerating system and equipment platform thereof | |
| CN220601645U (en) | Refrigerating equipment with air inlet surfaces and air exhaust surfaces orthogonally arranged double air channels and equipment platform thereof | |
| CN220453820U (en) | Air conditioner host and equipment platform adopting preposed fan wall exhaust cavity small-area exhaust outlet | |
| CN220552011U (en) | Air conditioner host with orthogonal air inlet surface and air outlet surface and equipment platform thereof | |
| CN219756527U (en) | Fin tube heat exchanger and multi-system heavy-load air conditioner host and equipment platform thereof | |
| CN220103273U (en) | Fin tube heat exchanger and air conditioner host machine, system and equipment platform thereof | |
| CN220852420U (en) | Main unit equipment integrating double-air-duct air conditioner and air energy water heater and equipment platform thereof | |
| CN219841605U (en) | Air conditioner host machine with bottom plate provided with air supplementing notch and fold line type finned tube heat exchanger assembly | |
| CN113932321A (en) | Narrow facade air conditioner outer unit of high-speed air-out | |
| CN220552013U (en) | Air conditioner water heater integration host computer of single channel wind path and equipment platform thereof | |
| CN220669645U (en) | Refrigerating equipment with air inlet surface and air exhaust surface orthogonally arranged single air duct and equipment platform | |
| CN116772307A (en) | Air conditioner host computer of fan vertical arrangement and equipment platform thereof | |
| CN116576514A (en) | Outer corridor type equipment platform adopting zigzag type finned tube heat exchanger air conditioner host | |
| CN219841603U (en) | Air conditioner host computer of three-dimensional air supply and equipment platform thereof | |
| CN219841602U (en) | Air conditioner host computer that many negative pressure chamber set up along long limit and equipment platform thereof | |
| CN221005315U (en) | Main unit and equipment platform for fusing rear single-air-duct double-refrigerating system of fan | |
| CN117212927A (en) | Main unit fusion body of fan rear-mounted double-air-duct double-refrigerating system and equipment platform thereof | |
| CN116697464A (en) | Fin tube heat exchanger assembly, air conditioner host and air conditioner system thereof | |
| CN116857725A (en) | Main unit equipment with air inlet surface and air exhaust surface provided with double air channels and double refrigeration systems in orthogonal mode and equipment platform of main unit equipment |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| GR01 | Patent grant | ||
| GR01 | Patent grant |