CN219064239U - Plate heat exchanger and air conditioner - Google Patents
Plate heat exchanger and air conditioner Download PDFInfo
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- CN219064239U CN219064239U CN202320005850.5U CN202320005850U CN219064239U CN 219064239 U CN219064239 U CN 219064239U CN 202320005850 U CN202320005850 U CN 202320005850U CN 219064239 U CN219064239 U CN 219064239U
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Abstract
The utility model belongs to the technical field of heat exchangers, and relates to a plate-type heat exchanger, which comprises a heat exchanger body, wherein the heat exchanger body comprises a plurality of heat exchange plates which are mutually pressed and installed, heat exchange channels are formed between adjacent heat exchange plates, one side of the heat exchanger body is provided with a refrigerant inlet channel, a refrigerant outlet channel, a medium inlet channel to be heat exchanged and a medium outlet channel to be heat exchanged which extend into the heat exchanger body, and the area of the plurality of heat exchange plates gradually decreases from the refrigerant inlet channel to the extending direction in the heat exchanger body. The utility model also provides an air conditioner comprising the plate heat exchanger. The utility model provides a plate heat exchanger and an air conditioner, which solve the problems of high pressure drop and low efficiency of the plate heat exchanger.
Description
Technical Field
The utility model belongs to the technical field of heat exchangers, and relates to a plate heat exchanger.
Background
At present, the main problems of the plate heat exchanger are large medium flow resistance and uneven medium flow distribution. Among them, the problem of uneven flow distribution of the medium is particularly remarkable. When a plate heat exchanger is used as an evaporator, refrigerant maldistribution is mainly caused by two mechanisms, namely pressure drop at the inlet angular pore channels of the plate heat exchanger and phase separation of the medium in the inlet angular pore channels. The pressure drop caused by the angular orifice channels is caused by different pressure distribution in the inlet and outlet angular orifice channels, so that the pressure drop at the two ends of the flow channel is uneven, and the flow velocity of the refrigerant is influenced. Thus, the flow through the different flow channels of the plate heat exchanger is not the same. The phase separation in the inlet angular pore channels is mainly due to the different thermophysical properties of the liquid and vapor refrigerants, particularly the different densities of the liquid and vapor refrigerants, resulting in different degrees of thermal expansion exerting different forces on the two phases, for example, resulting in different inertial and gravitational forces. Therefore, the static pressure in the angular hole channel of the plate heat exchanger, whether the angular hole channel is an inlet angular hole channel or an outlet angular hole channel, is increased along with the increase of the axial position of the angular hole, so that the pressure drop of the plate heat exchanger is large and the efficiency is low when the conventional plate heat exchanger is used, and the use effect of the plate heat exchanger is affected.
Disclosure of Invention
In view of the above, the utility model provides a plate heat exchanger, which solves the technical problems of large pressure drop and low efficiency of the existing plate heat exchanger, and further improves the overall performance of the plate heat exchanger.
In order to solve the above-mentioned problems, according to one aspect of the present application, the present utility model provides a plate heat exchanger, including a heat exchanger body, the heat exchanger body including a plurality of heat exchange fins mounted in compression with each other, heat exchange channels being formed between adjacent heat exchange fins, one side of the heat exchanger body being provided with a refrigerant inlet channel, a refrigerant outlet channel, a medium inlet channel to be heat exchanged and a medium outlet channel to be heat exchanged extending into the heat exchanger body, the plurality of heat exchange fins gradually decreasing in area in an extending direction from the refrigerant inlet channel into the heat exchanger body.
In some embodiments, at least one of the refrigerant inlet channel and the medium to be heat exchanged inlet channel has a gradually decreasing aperture along the direction of extension into the heat exchanger body.
In some embodiments, at least one of the refrigerant outlet channel and the medium to be heat exchanged outlet channel has a gradually decreasing aperture along the direction of extension into the heat exchanger body.
In some embodiments, the spacing between the plurality of heat exchange fins decreases progressively from the refrigerant inlet channel in the direction of extension into the heat exchanger body.
In some embodiments, the plurality of heat exchanger plates are similarly shaped, with midpoints of the plurality of heat exchanger plates lying on the same axis.
In some embodiments, the plurality of heat exchange plates are made of copper alloy.
In some embodiments, the refrigerant inlet channel, the refrigerant outlet channel, the medium inlet channel to be heat exchanged and the medium outlet channel to be heat exchanged are located at the lowest part of the channels on a horizontal plane when mounted.
In some embodiments, the diameters of the refrigerant inlet channel, the refrigerant outlet channel, the medium inlet channel to be heat exchanged, or the medium outlet channel to be heat exchanged are determined by the following formula:
wherein Y represents the diameter of a refrigerant inlet channel, a refrigerant outlet channel, a medium inlet channel to be heat-exchanged or a medium outlet channel to be heat-exchanged, D represents the angular hole diameter of the last heat exchange plate of the plate heat exchanger, D represents the angular hole diameter of the first heat exchange plate of the plate heat exchanger, and L represents the length of a header pipe of the plate heat exchanger.
In some embodiments, the plate heat exchanger is a herringbone plate heat exchanger or a point wave plate heat exchanger.
In order to solve the above-mentioned problems, according to another aspect of the present application, the present utility model also provides an air conditioner comprising a plate heat exchanger as in any one of the first aspects.
Compared with the prior art, the plate heat exchanger provided by the utility model has at least the following beneficial effects:
the plate heat exchanger comprises a heat exchanger body, wherein the heat exchanger body comprises a plurality of heat exchange plates which are mutually pressed and installed, heat exchange channels are formed between the adjacent heat exchange plates, and heat transfer is carried out between the plurality of heat exchange plates through the heat exchange channels and the heat exchange plates so as to realize heat transfer between working media. One side of the heat exchanger body is provided with a refrigerant inlet channel, a refrigerant outlet channel, a heat exchange medium inlet channel and a heat exchange medium outlet channel which extend into the heat exchanger body, wherein the refrigerant inlet channel is used for introducing refrigerant into the heat exchanger body, the refrigerant outlet channel is used for outputting refrigerant outwards from the heat exchanger body, the heat exchange medium inlet channel is used for introducing heat exchange medium into the heat exchanger body, and the heat exchange medium outlet channel is used for outputting heat exchange medium outwards from the heat exchanger body.
When the plate heat exchanger is used, the areas of the heat exchange plates gradually decrease from the refrigerant inlet channel to the extending direction in the heat exchanger body, so that when the plate heat exchanger is used as an evaporator, the inlet refrigerant state is usually in a two-phase flow state of three stages of vertex angle vapor flow, vapor jet flow and liquid blocking flow, the top layer low-momentum vapor refrigerant is easy to enter a branch pipe near the inlet, the high-momentum liquid refrigerant on the bottom layer moves towards the tail end in a biasing way, and the gas refrigerant mainly exists in the vertex angle of the inlet angle hole channel and the first flow channels. Therefore, through gradual change of the area of the plate, namely gradual reduction of the area of the plurality of heat exchange plates in the extending direction from the refrigerant inlet channel to the heat exchanger body, the heat exchange area of the first channels close to the inlet channel can be increased, the length of the two-phase region is further increased, and the heat exchange performance is improved. Meanwhile, the overall flow path of the plate heat exchanger is reduced due to gradual area change, so that the pressure drop caused by the flow channels is reduced. The total pressure drop of the plate heat exchanger will also decrease.
In another aspect, the air conditioner provided by the utility model is designed based on the plate heat exchanger, and the beneficial effects of the plate heat exchanger are referred to as beneficial effects of the plate heat exchanger, and are not described in detail herein.
The foregoing description is only an overview of the present utility model, and is intended to provide a better understanding of the present utility model, as it is embodied in the following description, with reference to the preferred embodiments of the present utility model and the accompanying drawings.
Drawings
In order to more clearly illustrate the technical solutions of the embodiments of the present utility model, the drawings required for the description of the embodiments will be briefly described below, and it is obvious that the drawings in the following description are some embodiments of the present utility model, and other drawings may be obtained according to these drawings without inventive effort for a person skilled in the art.
Fig. 1 is a schematic structural diagram of a first plate heat exchanger according to an embodiment of the present utility model;
fig. 2 is a schematic view of an overall arrangement structure of a plate heat exchanger according to an embodiment of the present utility model;
fig. 3 is a schematic diagram of an inlet micro-element structure of a plate heat exchanger according to an embodiment of the present utility model;
fig. 4 is a schematic diagram of an outlet micro-element structure of a plate heat exchanger according to an embodiment of the present utility model;
fig. 5 is a schematic diagram of a relationship between gradual change angle holes of a plate heat exchanger according to an embodiment of the present utility model;
fig. 6 is a schematic structural diagram of a second plate heat exchanger according to an embodiment of the present utility model;
fig. 7 is a schematic structural diagram of a third plate heat exchanger according to an embodiment of the present utility model;
fig. 8 is a schematic structural view of a fourth plate heat exchanger according to an embodiment of the present utility model;
fig. 9 is a schematic view of an internal structure of a plate heat exchanger according to an embodiment of the present utility model;
wherein: 100. a heat exchanger body; 101. a heat exchange plate; 110. a refrigerant inlet passage; 120. a refrigerant outlet passage; 130. an inlet channel for a medium to be heat-exchanged; 140. and a medium outlet channel to be heat-exchanged.
Detailed Description
In order to further describe the technical means and effects adopted for achieving the preset aim of the utility model, the following detailed description refers to the specific implementation, structure, characteristics and effects according to the application of the utility model with reference to the accompanying drawings and preferred embodiments. In the following description, different "an embodiment" or "an embodiment" do not necessarily refer to the same embodiment. Furthermore, the particular features, structures, or characteristics of one or more embodiments may be combined in any suitable manner.
In the description of the present utility model, it should be clear that the terms "first," "second," and the like in the description and claims of the present utility model and in the above-described figures are used for distinguishing between similar objects and not necessarily for describing a particular sequential or chronological order; the terms "vertical," "transverse," "longitudinal," "front," "rear," "left," "right," "upper," "lower," "horizontal," and the like are used for indicating an orientation or a positional relationship based on that shown in the drawings, and are merely for convenience of description of the present utility model, and do not mean that the apparatus or element referred to must have a specific orientation or position, and thus should not be construed as limiting the present utility model.
In the description of the present utility model, it should be noted that, unless explicitly specified and limited otherwise, the terms "mounted," "connected," and "connected" are to be construed broadly, and may be either fixedly connected, detachably connected, or integrally connected, for example; can be mechanically or electrically connected; can be directly connected or indirectly connected through an intermediate medium. The specific meaning of the above terms in the present utility model will be understood in specific cases by those of ordinary skill in the art.
Example 1
The utility model provides a plate heat exchanger, which comprises a heat exchanger body 100, wherein the heat exchanger body 100 comprises a plurality of heat exchange plates 101 which are mutually pressed and installed, heat exchange channels are formed between adjacent heat exchange plates 101, one side of the heat exchanger body 100 is provided with a refrigerant inlet channel 110, a refrigerant outlet channel 120, a medium inlet channel 130 to be heat exchanged and a medium outlet channel 140 to be heat exchanged, which extend into the heat exchanger body 100, and the areas of the plurality of heat exchange plates 101 gradually decrease from the refrigerant inlet channel 110 to the extending direction in the heat exchanger body 100.
Specifically, as shown in fig. 1, the heat exchanger body 100 is configured to exchange heat between a refrigerant and a working medium, the plurality of heat exchange fins 101 are stacked on each other, and heat exchange channels are provided between the plurality of heat exchange fins 101, so that heat exchange can be performed between the plurality of heat exchange fins 101 through the heat exchange channels. The refrigerant inlet channel 110 is for introducing refrigerant between the plurality of heat exchange plates 101, and the refrigerant outlet channel 120 is for discharging refrigerant from the refrigerant between the plurality of heat exchange plates 101. The medium inlet channel 130 is used for introducing medium to be heat-exchanged between the plurality of heat exchange plates 101, and the medium outlet channel 140 is used for discharging medium to be heat-exchanged from the medium to be heat-exchanged between the plurality of heat exchange plates 101.
In use, as shown in fig. 1, the plurality of heat exchange fins 101 gradually decrease in area from the refrigerant inlet channel 110 to the extending direction in the heat exchanger body 100, so that when the plate heat exchanger is used as an evaporator, the inlet refrigerant state is usually a two-phase flow state of three stages of top-angle vapor flow, vapor jet flow and liquid blocking flow, the top-layer low-momentum vapor refrigerant is easy to enter the branch pipe near the inlet, the high-momentum liquid refrigerant on the bottom layer moves towards the tail end, and the gas refrigerant mainly exists in the top angle of the inlet angular hole channel and the first few flow channels. Therefore, by gradually setting the plate area, that is, gradually decreasing the area of the plurality of heat exchange plates 101 in the extending direction from the refrigerant inlet channel 110 into the heat exchanger body 100, the heat exchange area of the first channels near the inlet channel can be increased, thereby increasing the length of the two-phase region and improving the heat exchange performance. Meanwhile, the overall flow path of the plate heat exchanger is reduced due to gradual area change, so that the pressure drop caused by the flow channels is reduced.
Referring to fig. 2, the plate heat exchanger is integrally arranged as shown in fig. 2, and factors affecting the uniform distribution of refrigerant in the plate heat exchanger are channel flow rate, angular hole channel pressure drop and total pressure drop. And the static pressure in the inlet angular hole channel or the outlet angular hole channel is increased along with the increase of the axial position of the angular hole.
As shown in fig. 3 to 5, the inlet angular orifice channel pressure drop calculation is represented by formula (1):
in the formula (1), wherein A represents the value of the cross-sectional area of the inlet header, A c Represents the value of the cross-sectional area of the flow channel, ρ represents the value of the fluid density, W represents the value of the velocity of the fluid at the inlet header, Δz represents the value of the infinitesimal length, U c The flow channel velocity value is represented by the flow channel velocity value,
indicating the value of the unit velocity component in the Z direction.
According to formula (2), the velocity of the flow channel is:
in the formula (2), L represents the header length, and n represents the number of flow channels.
Wherein, the liquid crystal display device comprises a liquid crystal display device,
conservation of momentum according to inlet angle aperture:
in the formula (4), P represents the pressure of the inlet header,
representing the unit pressure component in the Z direction, τ w Represents wall shear force, D represents inlet header diameter, W c Indicating the flow channel inlet velocity.
According to the Darcy-Weisbach formula:
τ w ＝fρ(W 2 /8) (5)
in formula (5), f represents the friction factor of the inlet header.
Substituting formula (5) into (4) to obtain:
fluid axial velocity:
W c ＝βW (7)
in the formula (7), β represents the inlet header speed ratio.
Inlet angular orifice passage pressure drop:
as shown in fig. 4, the channel pressure drop for the outlet angular aperture was calculated:
conservation of outlet angular aperture mass:
in the formula (10), A * Represents the cross-sectional area of the outlet header, W * Indicating the outletThe velocity of the header is such that,
representing a unit velocity component in the Z direction.
Flow channel speed:
according to equations (2) and (11):
wherein, the liquid crystal display device comprises a liquid crystal display device,
conservation of angular hole momentum:
in formula (14), P * Representing the pressure of the inlet header,
representing the unit pressure component in the Z direction, τ w * Representing wall shear force, D * Represents the inlet header diameter, W c * Indicating the flow channel inlet velocity.
According to the Darcy-Weisbach formula:
τ w * ＝fρ(W *2 /8) (15)
in formula (15), f * Representing the friction factor of the outlet header.
Substituting equation (15) into equation (14):
fluid axial velocity:
W c * ＝β * W * (17)
in formula (17), β * Indicating the outlet header speed ratio.
Outlet angular orifice passage pressure drop:
the calculating process of the flow non-uniformity coefficient comprises the following steps:
subtracting equation (19) from equation (9):
neglecting friction:
the relationship of pressure drop to channel flow rate is expressed by equation (22):
in formula (22), ζ c Indicating the total pressure drop loss coefficient of the flow channel.
Non-dimensionalization processing is performed by equation (24):
in the formula (24), p represents pressure dimensionality, w represents velocity dimensionality, μ c The channel speed is dimensionless, and z is dimensionless.
The method can obtain the following steps:
the flow non-uniformity coefficient is expressed as:
in the formula (28), m represents a characteristic parameter.
In a specific embodiment, the plurality of heat exchange fins 101 gradually decrease in area in the extending direction from the refrigerant inlet channel 110 into the heat exchanger body 100, and at least one of the refrigerant inlet channel 110 and the medium inlet channel 130 to be heat exchanged gradually decreases in aperture in the extending direction into the heat exchanger body 100.
Specifically, as shown in fig. 6, the plurality of heat exchange fins 101 of the plate heat exchanger gradually decrease in area in the extending direction from the refrigerant inlet channel 110 into the heat exchanger body 100, so that the overall flow stroke of the plate heat exchanger decreases, and therefore, the pressure drop when the refrigerant and the medium to be heat exchanged flow in the flow passage in the plate heat exchanger decreases, improving the use effect of the plate heat exchanger. Meanwhile, the areas of the heat exchange plates 101 are arranged to be of gradual change structures, so that the heat exchange area of the first channels close to the inlet channel can be increased, the length of a two-phase region is further increased, the heat exchange performance is improved, and the use effect of the plate heat exchanger is improved.
Meanwhile, as shown in fig. 2, by setting at least one of the refrigerant inlet passage 110 and the medium inlet passage 130 to be heat-exchanged as a tapered angular hole passage, the initial values of the diameters of the refrigerant inlet passage 110 and the medium inlet passage 130 to be heat-exchanged are equal to the values of the diameters of the original plate heat exchanger, and the aperture of at least one of the refrigerant inlet passage 110 and the medium inlet passage 130 to be heat-exchanged is gradually reduced in the extending direction into the heat exchanger body 100. As can be seen from equation (9), the inlet diameter decreases and the pressure drop across the inlet angular orifice passage decreases. The total pressure drop in the plate heat exchanger can be expressed as: p=p in +P L +P out Wherein P is in Representing the pressure drop at the inlet angular aperture, P L Representing the pressure drop at the flow channel, P out Representing the pressure drop at the outlet angular aperture, the total pressure drop of the plate heat exchanger will also decrease. As can be seen from the formula (28), the cross-sectional flow area of the inlet is reduced, the flow non-uniformity coefficient is reduced, the flow of each flow channel is completely equal as the flow non-uniformity coefficient is zero, and the fluid is completely uniformly distributed in the plate heat exchanger, and the larger the value is, the worse the flow distribution uniformity is. Thus, by gradually decreasing the aperture of at least one of the refrigerant inlet channel 110 and the medium inlet channel 130 to be heat exchanged in the extending direction into the heat exchanger body 100, the flow distribution in the plate heat exchanger is made more uniform.
At least one of the refrigerant inlet channel 110 and the medium inlet channel 130 to be heat-exchanged in the embodiment of the application gradually decreases along the aperture towards the extending direction in the heat exchanger body 100, so that when the refrigerant inlet channel 110 and the medium inlet channel 130 to be heat-exchanged enter the heat exchanger body 100, the flow distribution in the plate heat exchanger is more uniform through the gradual change of the inlet diameter, the flow velocity in the angular hole channel can be balanced, and the heat exchange effect is improved. Meanwhile, by reducing the diameters of the refrigerant inlet channel 110 and the medium inlet channel 130 to be heat-exchanged, the pressure drop of the refrigerant inlet channel 110 and the medium inlet channel 130 to be heat-exchanged is reduced, and the efficiency of the plate heat exchanger is also improved.
In a specific embodiment, the plurality of heat exchange fins 101 gradually decrease in area in the extending direction from the refrigerant inlet channel 110 into the heat exchanger body 100, and at least one of the refrigerant outlet channel 120 and the medium outlet channel 140 to be heat exchanged gradually decreases in aperture in the extending direction into the heat exchanger body 100.
Specifically, as shown in fig. 7, the plurality of heat exchange fins 101 of the plate heat exchanger gradually decrease in area in the extending direction from the refrigerant inlet channel 110 into the heat exchanger body 100, so that the overall flow stroke of the plate heat exchanger decreases, and therefore, the pressure drop when the refrigerant and the medium to be heat exchanged flow in the flow passage in the plate heat exchanger decreases, improving the use effect of the plate heat exchanger. Meanwhile, the areas of the heat exchange plates 101 are arranged to be of gradual change structures, so that the heat exchange area of the first channels close to the inlet channel can be increased, the length of a two-phase region is further increased, the heat exchange performance is improved, and the use effect of the plate heat exchanger is improved.
Meanwhile, as shown in fig. 7, it is possible to obtain angular hole passages in which the refrigerant outlet passage 120 and the medium outlet passage 140 to be heat-exchanged are provided in gradual change, the initial values of the outlet diameter ends of the refrigerant outlet passage 120 and the medium outlet passage 140 to be heat-exchanged are equal to the pore diameter values of the original plate heat exchanger, and at least one of the refrigerant outlet passage 120 and the medium outlet passage 140 to be heat-exchanged gradually decreases in pore diameter along the extending direction into the heat exchanger body 100. As can be seen from the formula (19), when at least one of the refrigerant outlet channel 120 and the medium outlet channel 140 to be heat-exchanged is gradually reduced in the aperture in the extending direction into the heat exchanger body 100, the refrigerant outlet channel 120 and the medium outlet channel 140 to be heat-exchanged are the outlet channels of the plate heat exchanger, and when the average diameter of the outlet channels of the plate heat exchanger becomes large, the pressure drop of the outlet channels is reduced.
At the same time, at least one of the refrigerant outlet channel 120 and the medium to be heat-exchanged outlet channel 140 has a gradually decreasing aperture along the extending direction into the heat exchanger body 100, so that the outlet angular hole channel follows the flow of the fluid in the fluid flow direction, through which the fluid flowsThe diameter of the pipeline is gradually increased, and the flow velocity in the outlet angular hole channel can be balanced by gradually increasing the diameter of the outlet angular hole, so that vortex areas in the outlet angular hole channel, namely, vortex in the refrigerant outlet channel 120 and the medium to be heat-exchanged outlet channel 140 are effectively eliminated, the flow field of the refrigerant and the medium to be heat-exchanged along the axial direction of the angular hole channel is gradually uniform, and the uniformity of the flow of the fluid in the plate heat exchanger is improved. Since the total pressure drop in the plate heat exchanger is: p=p in +P L +P out The total pressure drop of the plate heat exchanger will thus also decrease. As can be seen from the formula (28), the increase in the sectional area of the outlet channel average flow passage of the plate heat exchanger causes the flow non-uniformity coefficient to decrease, and therefore, by setting the outlet channel average flow passage sectional area of the plate heat exchanger to be gradually increased, that is, when at least one of the refrigerant outlet channel 120 and the medium outlet channel 140 to be heat-exchanged is gradually decreased in the aperture along the extending direction into the heat exchanger body 100, the flow distribution in the plate heat exchanger is more uniform, and the use effect of the plate heat exchanger can be improved.
In a specific embodiment, the plurality of heat exchange fins 101 gradually decrease in area in the direction of extension from the refrigerant inlet channel 110 into the heat exchanger body 100, at least one of the refrigerant inlet channel 110 and the medium inlet channel 130 to be heat exchanged gradually decreases in pore diameter in the direction of extension into the heat exchanger body 100, and at least one of the refrigerant outlet channel 120 and the medium outlet channel 140 to be heat exchanged gradually decreases in pore diameter in the direction of extension into the heat exchanger body 100.
Specifically, as shown in fig. 8, the plurality of heat exchange fins 101 of the plate heat exchanger gradually decrease in area in the extending direction from the refrigerant inlet channel 110 into the heat exchanger body 100, so that the overall flow stroke of the plate heat exchanger decreases, and therefore, the pressure drop when the refrigerant and the medium to be heat exchanged flow in the flow passage in the plate heat exchanger decreases, improving the use effect of the plate heat exchanger. Meanwhile, the areas of the heat exchange plates 101 are arranged to be of gradual change structures, so that the heat exchange area of the first channels close to the inlet channel can be increased, the length of a two-phase region is further increased, the heat exchange performance is improved, and the use effect of the plate heat exchanger is improved.
Similarly, as shown in fig. 8, the apertures of the refrigerant inlet channel 110, the medium inlet channel 130 to be heat-exchanged 130, the refrigerant outlet channel 120 and the medium outlet channel 140 to be heat-exchanged are gradually reduced along the extending direction into the heat exchanger body 100, so that the pressure drop of the inlet channel and the outlet channel of the plate heat exchanger is reduced, and the flow non-uniformity coefficient of the plate heat exchanger is reduced, so that the flow distribution in the plate heat exchanger is more uniform.
In a specific embodiment, the spacing between the plurality of heat exchange fins 101 decreases gradually from the refrigerant inlet channel 110 toward the extending direction inside the heat exchanger body 100.
Specifically, by gradually decreasing the intervals between the plurality of heat exchange plates 101 from the refrigerant inlet channel 110 toward the direction of extension in the heat exchanger body 100, so that the interval inlets between the plurality of heat exchange plates 101 near the inlet of the refrigerant inlet channel 110 are larger, the interval inlets between the plurality of heat exchange plates 101 far from the inlet of the refrigerant inlet channel 110 are smaller, so that the volume of the refrigerant or the medium to be heat exchanged between the plurality of heat exchange plates 101 in the direction of extension from the refrigerant inlet channel 110 toward the inside of the heat exchanger body 100 is gradually decreased, the overall flow stroke of the plate heat exchanger can be further reduced, the pressure drop in the plate heat exchanger is reduced, and the efficiency of the plate heat exchanger in use is improved.
In a particular embodiment, the plurality of heat exchanger plates 101 are similarly shaped, with midpoints of the plurality of heat exchanger plates 101 lying on the same axis.
Specifically, by setting the shapes of the heat exchange plates 101 to be similar structures, the heat exchange plates 101 are in uniform transition, so that the flow of the internal fluid medium of the plate heat exchanger is smoother, the pressure drop of the fluid flow in the plate heat exchanger is reduced, and the use effect of the plate heat exchanger is improved. Meanwhile, the midpoints of the heat exchange plates 101 are positioned on the same axis, so that fluid medium in the heat exchange plates 101 can flow stably, the lifting resistance of the fluid medium flowing in the plate heat exchanger is reduced, and the use effect of the plate heat exchanger is improved.
In a specific embodiment, the plurality of heat exchange plates 101 are made of copper alloy.
Specifically, each heat exchange plate 101 is made of copper alloy, so that the heat exchange efficiency of each heat exchange plate 101 is improved, and the use effect of the plate heat exchanger is improved.
In a specific embodiment, the refrigerant inlet channel 110, the refrigerant outlet channel 120, the medium inlet channel 130 to be heat exchanged and the medium outlet channel 140 to be heat exchanged are located at the lowest part of the channels in a horizontal plane when mounted.
Specifically, as shown in fig. 9, when the refrigerant inlet channel 110, the refrigerant outlet channel 120, the medium inlet channel 130 to be heat-exchanged and the medium outlet channel 140 to be heat-exchanged are installed, the lowest position of the channels can be located on the horizontal plane, so that the resistance of the fluid flowing through the refrigerant inlet channel 110, the refrigerant outlet channel 120, the medium inlet channel 130 to be heat-exchanged and the medium outlet channel 140 to be heat-exchanged is lower, the pressure drop of the fluid in the plate heat exchanger passing through the refrigerant inlet channel 110, the refrigerant outlet channel 120, the medium inlet channel 130 to be heat-exchanged and the medium outlet channel 140 to be heat-exchanged is improved, and the use effect of the plate heat exchanger is improved.
In a specific embodiment, the diameters of the refrigerant inlet channel 110, the refrigerant outlet channel 120, the medium inlet channel 130 to be heat exchanged or the medium outlet channel 140 to be heat exchanged are determined by the following formula:
where Y represents the diameter of the refrigerant inlet channel 110, the refrigerant outlet channel 120, the medium inlet channel 130 or the medium outlet channel 140 to be heat-exchanged, D represents the angular hole diameter of the last heat exchanger plate of the plate heat exchanger, D represents the angular hole diameter of the first heat exchanger plate of the plate heat exchanger, and D represents the header length of the plate heat exchanger.
Specifically, the diameter values of the respective refrigerant inlet channels 110, the refrigerant outlet channels 120, the medium inlet channels 130 or the medium outlet channels 140 to be heat-exchanged can be determined by the formula (29), so that the plate heat exchanger can be manufactured conveniently.
In a specific embodiment, the plate heat exchanger is a herringbone plate heat exchanger or a point wave plate heat exchanger, so that the use effect of the herringbone plate heat exchanger or the point wave plate heat exchanger can be improved.
Example 2
The embodiment of the application also provides an air conditioner which comprises the plate heat exchanger.
In this embodiment of the application, through the application of the above-mentioned plate heat exchanger on the air conditioner, this plate heat exchanger can improve the result of use of air conditioner.
In summary, it is easily understood by those skilled in the art that the above-mentioned advantageous features can be freely combined and overlapped without conflict.
The above is only a preferred embodiment of the present utility model, and the present utility model is not limited in any way, and any simple modification, equivalent variation and modification made to the above embodiment according to the technical substance of the present utility model still falls within the scope of the technical solution of the present utility model.
Claims (10)
1. The utility model provides a plate heat exchanger, its characterized in that, includes the heat exchanger body, the heat exchanger body is including compressing tightly a plurality of heat transfer fins of installation each other, forms the heat transfer passageway between the adjacent heat transfer fin, one side of heat exchanger body is equipped with and extends to refrigerant inlet channel, refrigerant outlet channel, wait heat transfer medium inlet channel and wait heat transfer medium outlet channel in the heat exchanger body, a plurality of the heat transfer fin is followed refrigerant inlet channel to the internal extension direction of heat exchanger goes up the area and reduces gradually.
2. A plate heat exchanger according to claim 1, wherein at least one of the refrigerant inlet channel and the medium inlet channel to be heat exchanged is tapered in pore size in the direction of extension into the heat exchanger body.
3. A plate heat exchanger according to claim 1 or 2, wherein at least one of the refrigerant outlet channel and the medium outlet channel to be heat exchanged is tapered in pore size in the direction of extension into the heat exchanger body.
4. A plate heat exchanger according to claim 3, wherein the spacing between a plurality of said heat exchanger plates decreases gradually from said refrigerant inlet channel in the direction of extension into said heat exchanger body.
5. A plate heat exchanger according to claim 4, wherein a plurality of said heat exchanger plates are similarly shaped, the midpoints of the plurality of said heat exchanger plates being located on the same axis.
6. A plate heat exchanger according to claim 5, wherein a plurality of said heat exchanger plates are made of copper alloy.
7. A plate heat exchanger according to claim 1, wherein the refrigerant inlet channel, the refrigerant outlet channel, the medium inlet channel to be heat exchanged and the medium outlet channel to be heat exchanged are located at the lowest level of the channels when installed.
8. A plate heat exchanger according to claim 7, wherein the diameter of the refrigerant inlet channel, the refrigerant outlet channel, the medium inlet channel or the medium outlet channel to be heat exchanged is determined by the formula:
wherein Y represents the diameter of the refrigerant inlet channel, the refrigerant outlet channel, the medium inlet channel to be heat-exchanged or the medium outlet channel to be heat-exchanged, D represents the angular hole diameter of the last heat exchange plate of the plate heat exchanger, D represents the angular hole diameter of the first heat exchange plate of the plate heat exchanger, and L represents the length of a header pipe of the plate heat exchanger.
9. A plate heat exchanger according to claim 8, characterized in that the plate heat exchanger is a herringbone plate heat exchanger or a point wave plate heat exchanger.
10. An air conditioner comprising a plate heat exchanger according to any one of claims 1 to 9.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202320005850.5U CN219064239U (en) | 2023-01-03 | 2023-01-03 | Plate heat exchanger and air conditioner |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202320005850.5U CN219064239U (en) | 2023-01-03 | 2023-01-03 | Plate heat exchanger and air conditioner |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN219064239U true CN219064239U (en) | 2023-05-23 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202320005850.5U Active CN219064239U (en) | 2023-01-03 | 2023-01-03 | Plate heat exchanger and air conditioner |
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| Country | Link |
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| CN (1) | CN219064239U (en) |
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2023
- 2023-01-03 CN CN202320005850.5U patent/CN219064239U/en active Active
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