Patent Grant
7066243
This application claims priority to Japanese Patent Application No. 2001-183062 filed on Jun. 18, 2001 and U.S. Provisional application No. 60/303,145 filed on Jul. 6, 2001, the disclosure of which is incorporated by reference in its entirety.
The present invention relates to, for example, an evaporator for car air-conditioners or room air-conditioners, a manufacturing method thereof, a header member for an evaporator and a refrigeration system.
A refrigeration system for car air-conditioners has a refrigeration cycle. In this cycle, a gaseous refrigerant of high temperature and high pressure sent out of a compressor is condensed by a condenser and then made into mist-like refrigerant including a gaseous phase and a liquid phase by decompressing means such as an expansion valve. Then, the mist-like refrigerant evaporates while passing through an evaporator. Thereafter, the evaporated refrigerant returns to the compressor.
As a conventional evaporator used in the aforementioned refrigeration system, a laminated type evaporator is mainly used. The laminated type evaporator includes a plurality of tubular elements laminated in laminating direction and fins each interposed between the adjacent tubular elements, wherein each tubular element is formed by coupling a pair of plate-shaped formed plates in a face-to-face manner.
This kind of laminated type evaporator is large in cooling capacity and is low in air-side pressure loss, and therefore has excellent characteristics. In recent years, in view of an odor problem of an inside of a car or the like, an odor removal filter is sometimes installed in front of the evaporator. In this case, in order to secure the mounting space for such a filter, the evaporator tends to be required to reduce the thickness.
In meeting such a demand of reducing the thickness of the aforementioned laminated type evaporator, the following drawbacks have became clear.
First, since each tubular element having heat exchanging passages is formed by coupling a pair of plate-shaped formed plates formed by drawing processing using a press in a face-to-face manner, the portions where the pair of formed plates directly contact, i.e., the portions other than the heat exchanging passages, likely increase. Consequently, the cross-sectional area of the refrigerant passages decrease, which may cause high refrigerant side pressure drop and deteriorate the performance. As this countermeasure, it is considered to increase the height of the refrigerant passage by increasing the drawing amount of the formed plate to thereby enlarge the cross-sectional area of the passage. However, according this proposal, the tubular element becomes thick, and therefore the air-side passage between the adjacent tubular elements becomes smaller, resulting in a reduced size of the fin disposed in the air-side passage. Consequently, there is a possibility that the air-side pressure drop increases and that the heat transferring area of the fin decreases, which in turn causes a deterioration of the performance.
Second, in the aforementioned laminated type evaporator, the fin does not comes into contact with a portion where the pair of formed plates directly contact each other, and therefore surface efficiency deteriorates. Accordingly, the more the thickness of the tubular element becomes, the more the rate of non-contact portion of the fin increases. This may cause a deterioration of the cooling performance.
Third, in the aforementioned laminated type evaporator, since the tank portion and the tube portion (heat exchanging medium passage portion) are integrally formed in the plate-shaped formed plate, the tank portion where higher pressure resistance is required is also formed by a drawing processing. Accordingly, the thickness of the tank portion tends to become thinner than that of the tube portion (heat exchange medium passage portion). Accordingly, It is necessary to design the wall thickness on the basis of the tank portion. As a result, even if the tube portion has enough pressure resistance, it is impossible to further reduce the wall thickness, which may not meet the demand of reducing weight.
As will be apparent from the above, in a laminated type evaporator, it is difficult to further reduce the thickness while achieving sufficient performance.
The present invention was made in view of the aforementioned circumstances, it is an object of the present invention to provide an evaporator capable of reducing the weight and the size while maintaining sufficient heat exchanging performance, the manufacturing method of the evaporator, a header member for the evaporator and a refrigeration system.
Another objects of the present invention will be apparent from the following explanation.
According to the first aspect of the present invention, an evaporator comprises:
a core including an upstream-side heat exchanging tube group and a downstream-side heat exchanging tube group arranged front and rear, each of the heat exchanging tube groups including a plurality of heat exchanging tubes disposed parallel with each other at certain intervals;
an inlet-side tank disposed along one end side of the upstream-side heat exchanging tube group;
an outlet-side tank disposed along one end side of the downstream-side heat exchanging tube group; and
a refrigerant turning member disposed along the other end side of both the heat exchanging tube groups,
wherein each one end of the heat exchanging tubes constituting the upstream-side heat exchanging tube group is connected to the inlet-side tank, while the other end thereof is connected to the refrigerant turning member, and
wherein each one end of the heat exchanging tubes constituting the downstream-side heat exchanging tube group is connected to the outlet-side tank, while the other end thereof is connected to the refrigerant turning member,
whereby refrigerant flowed into the inlet-side tank is introduced into the outlet-side tank via the upstream-side heat exchanging tube group, the refrigerant turning member and the downstream-side heat exchanging tube group, while the refrigerant passing through both the heat exchanging tube groups evaporates by exchanging heat with ambient air.
In the evaporator of the present invention, since the refrigerant passage is formed into a U-shape by the upstream-side and downstream-side heat exchanging tube groups, the refrigerant pressure drop can be decreased. Accordingly, the refrigerant passage cross-sectional area can be reduced, and the tube height of the heat exchanging tube can be lowered. Furthermore, since the tube height can be lowered, the number of heat exchanging tubes can be increased without increasing the core dimension, resulting in an enhanced refrigerant dispersibility.
In the present invention, it is preferable that the inlet-side tank is provided with refrigerant distributing resistance means which distributes the refrigerant in a longitudinal direction of the inlet-side tank, or the outlet-side tank is provided with uneven-distribution-flow preventing resistance means which prevents uneven-distribution-flow of refrigerant.
In cases where these structures are adopted, the refrigerant passing through the heat exchanging tube groups is distributed equally throughout the core, and therefore the heat exchange can be performed efficiently throughout the core.
In order to attain the aforementioned object, according to the second aspect of the present invention, an evaporator comprises:
a core including an upstream-side heat exchanging tube group and a downstream-side heat exchanging tube group arranged front and rear, each of the heat exchanging tube groups including a plurality of heat exchanging tubes disposed parallel with each other at certain intervals;
an inlet-and-outlet-side header member disposed along one end side of both the heat exchanging tube groups; and
a refrigerant-turn-side header member disposed along the other end side of both the heat exchanging tube groups,
wherein an inside of the inlet-and-outlet-side header member is divided front and rear by a partition into a front-side portion and a rear-side portion, wherein the front-side portion constitutes an inlet-side tank and the rear-side portion constitutes an outlet-side tank,
wherein one end of each of the heat exchanging tubes constituting the upstream-side heat exchanging tube group is connected to the inlet-side tank of the inlet-and-outlet-side header member, while the other end thereof is connected to the refrigerant-turn-side header member, and
wherein one end of each of the heat exchanging tubes constituting the downstream-side heat exchanging tube group is connected to the outlet-side tank of the inlet-and-outlet-side header member, while the other end thereof is connected to the refrigerant-turn-side header member,
whereby refrigerant flowed into the inlet-side tank is introduced into the outlet-side tank via the upstream-side heat exchanging tube group, the refrigerant-turn-side member and the downstream-side heat exchanging tube group, while the refrigerant passing through both the heat exchanging tube groups evaporates by exchanging heat with ambient air.
In the evaporator of this invention, since the refrigerant passage is formed into a simple U-shape like in the aforementioned evaporator, the refrigerant flow resistance can be decreased, resulting in enhanced refrigerant dispersibility.
In the evaporator according to the present invention, it is preferable that the inlet-and-outlet-side header member includes an inlet-and-outlet-side header plate to which one end of each of the heat exchanging tubes is fixed in a penetrated manner and an inlet-and-outlet-side header cover attached to the header plate so as to cover one surface side of the header plate.
Furthermore, in the present invention, it is preferable that the refrigerant-turn-side header member includes a refrigerant-turn-side header plate to which the other end of each of the heat exchanging tubes is fixed in a penetrated manner and a refrigerant-turn-side header cover attached to the header plate so as to cover the other surface of the header plate.
In the present invention, it is preferable to employ the following structures in order to enhance the refrigerant dispersibility.
That is, in the present invention, it is preferable that refrigerant distributing resistance means which distributes the refrigerant in a longitudinal direction of the inlet-side tank is provided in an inside of the inlet-side tank.
As the aforementioned refrigerant distributing resistance means, it is possible to employ a refrigerant distributing resistance plate which divides the inlet-side tank into an upper space and a lower space and has a plurality of refrigerant passage apertures formed at intervals along the longitudinal direction of the inlet-side tank.
Furthermore, it is preferable that the plurality of refrigerant passage apertures of the refrigerant distributing resistance plate include apertures different in size.
Furthermore, it is preferable that the inlet-and-outlet-side header member has a refrigerant inlet for introducing refrigerant into the inlet-side tank, and wherein the plurality of refrigerant passage apertures of the refrigerant distributing resistance plate are formed so that the refrigerant passage aperture increases in size as it goes away from the refrigerant inlet, or that the refrigerant inlet is formed at a longitudinal middle position of the inlet-side tank, and wherein the refrigerant passage apertures formed in the refrigerant distributing resistance plate and located apart from the refrigerant inlet is formed to have a size larger than a size of the refrigerant passage aperture located near the refrigerant inlet.
In the present invention, it is also possible to employ the structure that the refrigerant inlet is provided at a longitudinal end portion of the inlet-side tank.
In the present invention, it is preferable to employ the following structures in order to further enhance the refrigerant dispersibility.
That is, in the present invention, it is preferable that uneven-distribution-flow preventing resistance means for preventing uneven-refrigerant-flow is provided within the outlet-side tank of the inlet-and-outlet-side header member.
As this uneven-distribution-flow preventing resistance means, it is preferable to employ an uneven-distribution-flow preventing resistance plate which divides the outlet-side tank into an upper space and a lower space and has a plurality of refrigerant passage apertures formed at intervals along a longitudinal direction of the outlet-side tank.
Furthermore, in the present invention, it is preferable that a distance between adjacent refrigerant passage apertures formed in the uneven-distribution-flow preventing resistance plate falls within the range of 1 to 4 times as long as a distance between adjacent heat exchanging tubes.
In cases where this structure is employed, the refrigerant can be flowed evenly thorough the entire core, resulting in enhanced refrigeration performance.
Furthermore, in the present invention, it is preferable that the refrigerant passage apertures formed in the uneven-distribution-flow preventing resistance plate are offset from a widthwise central portion of the heat exchanging tube toward a windward side relative to an air introducing direction.
In cases where this structure is employed, it is possible to prevent the liquefied refrigerant flow from the inlet-and-outlet-side header member, resulting in a stable expansion valve control.
In the present invention, it is more preferable that the inlet-and-outlet-side header member has a refrigerant outlet through which refrigerant flows out of the outlet-side tank, and wherein a cross-sectional area of a refrigerant passage aperture located in the most distant position from the refrigerant outlet among the refrigerant passage apertures formed in the uneven-distribution-flow preventing resistance plate is set to 7 mm2 or less.
In cases where this structure is employed, the dispersibility of the refrigerant can be further enhanced.
Furthermore, in the present invention, it is possible to employ the structure that the refrigerant outlet is provided at a longitudinal middle portion of the outlet-side tank, or that the refrigerant outlet is provided at a longitudinal end portion of the outlet-side tank.
Furthermore, in the present invention, it is preferable that a cross-sectional area between the uneven-distribution-flow preventing resistance plate and an end portion of the heat exchanging tube in the outlet-side tank is 1 to 5 times as large as a passage cross-sectional area of the heat exchanging tube.
That is, by employing this structure, it is possible to prevent an increase of flow resistance between the uneven-distribution-flow preventing resistance plate and an end portion of the heat exchanging tube and secure an appropriate space in the header member.
In the present invention, it is preferable that a total cross-sectional area of the refrigerant passage apertures formed in the uneven-distribution-flow preventing resistance plate is larger than a total passage cross-sectional area of the heat exchanging tubes at the downstream-side heat exchanging tube group.
In cases where this structure is employed, it is possible to prevent an increase of flow resistance and further enhance the dispersibility of the refrigerant.
Furthermore, in the present invention, in order to prevent an increase of flow resistance and further enhance the dispersibility of the refrigerant, it is preferable that each of the refrigerant passage aperture formed in the uneven-distribution-flow preventing resistance plate is formed into a round shape, or that the refrigerant passage aperture formed in the uneven-distribution-flow preventing resistance plate is formed into an ellipse shape or a rectangular shape having a major axis along a width direction of the heat exchanging tube.
In the present invention, it is preferable that corresponding heat exchanging tubes of both the heat exchanging tube groups are integrally connected, or that the heat exchanging tube is an extruded tube obtained by extrusion molding.
In the present invention, it is possible to employ the structure that a tube height of the heat exchanging tube falls within the range of from 0.75 to 1.5 mm.
According to the third aspect of the present invention, an evaporator comprises:
a core including an upstream-side heat exchanging tube group and a downstream-side heat exchanging tube group arranged front and rear, each of the heat exchanging tube group including a plurality of heat exchanging tubes disposed parallel with each other at certain intervals;
an inlet-and-outlet-side header member disposed along one end side of both the heat exchanging tube groups; and
a refrigerant-turn-side header member disposed along the other end side of both the heat exchanging tube groups,
wherein an inside of the inlet-and-outlet-side header member is divided into an inlet-side tank and an outlet-side tank,
wherein the refrigerant-turn-side header member includes at least two press-formed metal plate members,
wherein an inside of the refrigerant-turn-side header member is divided into an inflow-side tank and an outflow-side tank by a refrigerant-turn-side partition, and both the tanks being communicated by communication apertures provided in the partition,
wherein one end of each of the heat exchanging tubes constituting the upstream-side heat exchanging tube group is connected to the inlet-side tank of the inlet-and-outlet-side header member, while the other end thereof is connected to the inflow-side tank of the refrigerant-turn-side header member, and
wherein one end of each of the heat exchanging tubes constituting the downstream-side heat exchanging tube group is connected to the outlet-side tank of the inlet-and-outlet-side header member, while the other end thereof is connected to the outflow-side tank of the refrigerant-turn-side header member,
whereby refrigerant flowed into the inlet-side tank is introduced into the outlet-side tank via the upstream-side heat exchanging tube group, the inflow-side tank, the apertures, the outflow-side tank and the downstream-side heat exchanging tube group, while the refrigerant passing through both the heat exchanging tube groups evaporates by exchanging heat with ambient air.
In the third aspect of the present invention, in the same way as in the first and second inventions, since the refrigerant passage is formed into a simple U-shape, the refrigerant pressure drop can be decreased, resulting in an enhanced refrigerant dispersibility. Furthermore, since the press-formed metal plate member is used as the inlet-and-outlet-side header member, the header material can be continuously manufactured from a coiled metal material, which can increase the productivity.
Furthermore, since the header material is constituted by a plate member, as this header material, it is possible to use a brazing sheet in which clad materials such as brazing materials or sacrificial materials laminated on at least one surface thereof. Thus, the brazability and corrosion resistance can be improved.
Furthermore, in the present invention, it is preferable that the refrigerant-turn-side header member includes a header plate to which one end of each of the heat exchanging tubes is fixed in a penetrated manner and a header cover attached to the header plate so as to cover one surface side of the header plate, and wherein the refrigerant-turn-side partition is formed by folding a widthwise middle portion of a metal plate member constituting the header cover along a longitudinal direction thereof.
That is, in cases where this structure is employed, since the partition can be integrally formed by press forming processing, the productivity can be further improved. Furthermore, since the partition is constituted by folded plate portions, enough strength can be achieved by the partition, resulting in further enhancing pressure resistance of the header member.
Furthermore, in the present invention, it is preferable that the refrigerant-turn-side partition has at a tip portion thereof engaging protrusions at certain intervals along a longitudinal direction thereof, wherein the header plate has at a widthwise middle portion thereof engaging apertures corresponding to the engaging protrusions at certain intervals along a longitudinal direction thereof, and wherein the engaging protrusions are inserted and fixed in the engaging apertures by caulking processing.
In cases where this structure is employed, the positioning of the header cover relative to the header plate can be performed more assuredly.
Furthermore, in the present invention, it is more preferable that the metal plate member constituting the refrigerant-turn-side header member is formed by an aluminum brazing sheet having an aluminum core and a brazing layer laminated on at least one side of the core.
That is, in cases where this structure is employed, the brazability of the entire evaporator can be further enhanced.
Furthermore, in the present invention, it is preferable that the brazing sheet has the brazing layer laminated at an external surface side thereof, and wherein the brazing layer contains zinc.
That is, in cases where this structure is employed, a sacrificial-corrosion layer can be formed on the external surface of the refrigerant-turn-side header member, resulting in an enhanced corrosion resistance.
Furthermore, in the present invention, it is preferable that a thickness of the header cover is thinner than that of the header plate.
That is, in cases where this structure is employed, the size and weight of the header member, or the entire evaporator, can be reduced while keeping enough pressure strength.
In the third aspect of the present invention, it is preferable that the inlet-and-outlet-side header member includes at least two press-formed metal plate members.
That is, in cases where this structure is employed, the productivity and brazability of the inlet-and-outlet-side header member can be further improved.
In the third aspect of the present invention, it is preferable to constitute the inlet-and-outlet-side header member as follows in the same way as in the refrigerant-turn-side header member.
That is, in the third aspect of the present invention, it is preferable that the inlet-and-outlet-side header member has a header plate to which an end portion of each of the exchanging tubes is fixed in a penetrated manner and a header cover attached to the header plate so as to cover one surface side thereof, and wherein the inlet-and-outlet-side partition is formed by folding a widthwise middle portion of a metal plate member constituting the header cover along a longitudinal direction thereof.
That is, in the third aspect of the present invention, it is preferable that the inlet-and-outlet-side partition has at a tip portion thereof engaging protrusions at certain intervals along a longitudinal direction thereof, wherein the header plate has at a widthwise middle portion thereof engaging apertures corresponding to the engaging protrusions at certain intervals along a longitudinal direction thereof, and wherein the engaging protrusions are inserted in and fixed to the engaging apertures by caulking processing.
Further, in the third aspect of the present invention, it is preferable that the metal plate member constituting the inlet-and-outlet-side header member is formed by an aluminum brazing sheet having a brazing layer laminated on at least one side thereof.
Further, in the third aspect of the present invention, it is preferable that the brazing sheet has the brazing layer laminated at an external surface side thereof, and wherein the brazing layer contains zinc.
Further, in the third aspect of the present invention, it is preferable that a thickness of the header cover is thinner than that of the header plate.
According to the fourth aspect of the present invention, an evaporator comprises:
a core including an upstream-side heat exchanging tube group and a downstream-side heat exchanging tube group arranged front and rear, each of the heat exchanging tube groups including a plurality of heat exchanging tubes disposed parallel with each other at certain intervals;
an inlet-and-outlet-side header member disposed along one end side of both the heat exchanging tube groups; and
a refrigerant-turn-side header member disposed along the other end side of both the heat exchanging tube groups,
wherein the inlet-and-outlet-side header member includes an inlet-and-outlet-side header plate, an inlet-and-outlet-side header cover attached to the header plate so as to cover one surface side of the header plate and a partition for dividing an inside of the inlet-and-outlet-side header member into an inlet-side tank and an outlet-side tank,
wherein the refrigerant-turn-side header member includes a refrigerant-turn-side header plate and a refrigerant-turn-side header cover attached to the header plate so as to cover one surface side of the header plate, one of the refrigerant-turn-side header plate and the refrigerant-turn-side header cover being formed by a press-formed metal plate member, and the other thereof being formed by an extruded molded article,
wherein one end of each of the heat exchanging tubes constituting the upstream-side heat exchanging tube group is fixed to the inlet-and-outlet-side header plate in a penetrated manner to thereby be connected to the inlet-side tank, while the other end thereof is connected to the refrigerant-turn-side header plate in a penetrated manner,
wherein one end of each of the heat exchanging tubes constituting the downstream-side heat exchanging tube group is fixed to the inlet-and-outlet-side header member to thereby be connected to the outlet-side tank, while the other end thereof is connected to the refrigerant-turn-side header member in a predetermined manner,
whereby refrigerant flowed into the inlet-side tank is introduced into the outlet-side tank via the upstream-side heat exchanging tube group, the refrigerant-turn-side header member and the downstream-side heat exchanging tube group, while the refrigerant passing through both the heat exchanging tube groups evaporates by exchanging heat with ambient air.
In the fourth aspect of the present invention, in the same way as in the third aspect of the present invention, since the refrigerant passage is formed into a simple U-shape, the refrigerant pressure drop can be reduced and the dispersibility of the refrigerant can be increased. Furthermore, in the refrigerant-turn-side header member, the productivity, brazability and corrosion resistance can be improved.
In the fourth aspect of the present invention, it is preferable that one of the inlet-and-outlet-side header plate and the inlet-and-outlet-side header cover is formed by a press-formed metal plate member and the other thereof is formed by an extruded molded article.
In cases where this structure is employed, in the inlet-and-outlet-side header cover, the productivity and brazability can also be improved.
According to the fifth aspect of the present invention, a method of manufacturing an evaporator comprises the steps of:
a step of preparing a plurality of heat exchanging tubes constituting an upstream-side heat exchanging tube group and a downstream-side heat exchanging tube group to be disposed front and rear;
a step of preparing an inlet-side tank to be disposed along one end side of the upstream-side heat exchanging tube group;
a step of preparing an outlet-side tank to be disposed along one end side of the downstream-side heat exchanging tube group;
a step of preparing a refrigerant turning member to be disposed along the other end side of both the heat exchanging tubes groups;
a step of brazing one end of each of the heat exchanging tubes constituting the upstream-side heat exchanging tube group to the inlet-side tank;
a step of brazing the other end of each of the heat exchanging tubes constituting the upstream-side heat exchanging tube group to the refrigerant turning member;
a step of brazing one end of each of the heat exchanging tubes constituting the downstream-side heat exchanging tube group; and
a step of brazing the other end of each of the heat exchanging tubes constituting the downstream-side heat exchanging tube group to the refrigerant turning member;
wherein refrigerant flowed into the inlet-side tank is introduced into the outlet-side tank by passing through the upstream-side heat exchanging tube group, the refrigerant turning member and the downstream-side heat exchanging tube group, and
wherein the refrigerant passing through both the heat exchanging tube groups constitutes a refrigerant circuit in which the refrigerant evaporates by exchanging heat with ambient air.
In the fifth aspect of the present invention, the evaporator according to the first aspect of the present invention can be manufactured assuredly.
In the fifth aspect of the present invention, it is preferable that the brazing steps are collectively performed by furnace brazing processing.
The sixth aspect of the present invention specifies one embodiment of the manufacturing process of the evaporator according to the second aspect of the present invention.
That is, according to the sixth aspect of the present invention, a method of manufacturing an evaporator comprises the steps of:
a step of preparing heat exchanging tubes constituting an upstream-side heat exchanging tube group and a downstream-side heat exchanging tube group to be disposed front and rear;
a step of preparing an inlet-and-outlet-side header member to be disposed along one end side of both the heat exchanging tube groups, wherein an inside of the header member is divided by a partition front and rear into one side space constituting an inlet-side tank and the other side space constituting an outlet-side tank;
a step of preparing a refrigerant-turn-side header member to be disposed along the other end side of both the heat exchanging tube groups;
a step of brazing one end of each of the heat exchanging tubes constituting the upstream-side heat exchanging tube group to an inlet-side tank of the inlet-and-outlet-side header;
a step of brazing the other end of each of the heat exchanging tubes constituting the upstream-side heat exchanging tube group to the refrigerant-turn-side header member;
a step of brazing one end of each of the heat exchanging tubes constituting the downstream-side heat exchanging tube group to the outlet-side tank of the inlet-and-outlet-side header; and
a step of brazing the other end of each of the heat exchanging tubes of the downstream-side heat exchanging tube group to the refrigerant-turn-side header member;
wherein refrigerant flowed into the inlet-side tank is introduced into the outlet-side tank by passing through the upstream-side heat exchanging tube group, the refrigerant-turn-side header member and the downstream-side heat exchanging tube group, and
wherein the refrigerant passing through both the heat exchanging tube groups constitutes a refrigerant circuit in which the refrigerant evaporates by exchanging heat with ambient air.
According to the sixth aspect of the present invention, the evaporator according to the second aspect of the present invention can be manufactured assuredly.
In the sixth aspect of the present invention, it is preferable that the brazing steps are collectively performed by furnace brazing processing.
The seventh aspect of the present invention specifies an embodiment of the manufacturing process of the evaporator according to the third aspect of the present invention.
That is, according to the seventh aspect of the present invention, the method comprises the steps of:
a step of preparing heat exchanging tubes constituting an upstream-side heat exchanging tube group and a downstream-side heat exchanging tube group to be disposed front and rear;
a step of preparing an inlet-and-outlet-side header member to be disposed along one end of both the heat exchanging tube groups, an inside of the header member being divided into an inlet-side tank and an outlet-side tank;
a step of preparing a refrigerant-turn-side header member to be disposed along the other end side of both the heat exchanging tube groups, the refrigerant-turn-side header member including at least two press-formed metal plate members, and an inside of the header member being divided by a refrigerant-turn-side partition into an inflow-side tank and an outflow-side tank, and the both tanks being communicated each other via communication apertures formed in the partition;
a step of brazing one end of each of the heat exchanging tubes constituting the upstream-side heat exchanging tube group to an inlet-side tank of the inlet-and-outlet-side header;
a step of brazing the other end of each of the heat exchanging tubes constituting the upstream-side heat exchanging tube group to an inflow-side tank of the refrigerant-turn-side header member;
a step of brazing one end of each of the heat exchanging tubes constituting the downstream-side heat exchanging tube group to the outlet-side tank of the inlet-and-outlet-side header; and
a step of brazing the other end of each of the heat exchanging tubes of the downstream-side heat exchanging tube group to an outflow-side tank of the refrigerant-turn-side header member;
wherein refrigerant flowed into the inlet-side tank is introduced into the outlet-side tank by passing through the upstream-side heat exchanging tube group, the inflow-side tank, the communication apertures, the outflow-side tank and the downstream-side heat exchanging tube group, and
wherein the refrigerant passing through both the heat exchanging tube groups constitutes a refrigerant circuit in which the refrigerant evaporates by exchanging heat with ambient air.
According to the seventh aspect of the present invention, the evaporator according to the third aspect of the present invention can be manufactured assuredly.
In the seventh aspect of the present invention, it is preferable that the brazing steps are collectively performed by furnace brazing processing.
The eighth aspect of the present invention specifies an embodiment of the manufacturing process of the evaporator according to the fourth aspect of the present invention.
According to the eighth aspect of the present invention, a method of manufacturing an evaporator comprises the steps of:
a step of preparing heat exchanging tubes constituting an upstream-side heat exchanging tube group and a downstream-side heat exchanging tube group to be disposed front and rear;
a step of preparing an inlet-and-outlet-side header member to be disposed along one end of both the heat exchanging tube groups, wherein the header member includes an inlet-and-outlet-side header plate, an inlet-and-outlet-side header cover attached to the header plate so as to cover one surface side thereof and a partition for dividing an inside of the inlet-and-outlet-side header member into an inlet-side tank and an outlet-side tank;
a step of preparing a refrigerant-turn-side header member to be disposed along the other end side of both the heat exchanging tube groups, wherein the refrigerant-turn-side header member includes a refrigerant-turn-side header plate and a refrigerant-turn-side header cover attached to the header plate so as to cover one side surface thereof, one of the refrigerant-turn-side header plate and the refrigerant-turn-side header cover being made of a press-formed metal plate, and the other thereof being made of an extruded molded article;
a step of brazing one end of each of the heat exchanging tubes constituting the upstream-side heat exchanging tube group to the header plate of the inlet-and-outlet-side header to thereby be connected to the inlet-side tank;
a step of brazing the other end of each of the heat exchanging tubes constituting the upstream-side heat exchanging tube group to the header plate of the refrigerant-turn-side header member;
a step of brazing one end of each of the heat exchanging tubes constituting the downstream-side heat exchanging tube group to the header plate of the inlet-and-outlet-side header to thereby be connected to the outlet-side tank; and
a step of brazing the other end of each of the heat exchanging tubes constituting the downstream-side heat exchanging tube group to the header plate of the refrigerant-turn-side header member;
wherein refrigerant flowed into the inlet-side tank is introduced into the outlet-side tank by passing through the upstream-side heat exchanging tube group, the refrigerant-turn-side header member and the downstream-side heat exchanging tube group, and
wherein the refrigerant passing through both the heat exchanging tube groups constitutes a refrigerant circuit in which the refrigerant evaporates by exchanging heat with ambient air.
According to the eight aspect of the present invention, the evaporator according to the fourth aspect of the present invention can be manufactured assuredly.
In the eighth aspect of the present invention, in order to improve the productivity, it is preferable that the brazing steps are collectively performed by furnace brazing processing.
Furthermore, in the eighth aspect of the present invention, it is preferable that a step of forming a zinc diffusion layer on a surface of each of the header members is performed by applying a flux containing zinc on the surface before performing the furnace brazing processing.
In this case, a sacrifice layer can be assuredly formed on the external surface of the header member, which can improve the corrosion resistance.
The ninth aspect of the present invention specifies an inlet-and-outlet-side header member applicable to the aforementioned third or fourth aspect of the present invention.
That is, according to the ninth aspect of the present invention, an inlet-and-outlet-side header member for an evaporator with a core including an upstream-side heat exchanging tube group and a downstream-side heat exchanging tube group disposed front and rear, each of heat exchanging tube group including a plurality of heat exchanging tubes arranged in parallel with each other at certain intervals, comprises:
a header plate for fixing an end portion of each of the heat exchanging tubes in a penetrated manner;
a header cover attached to the header plate so as to cover one surface side thereof; and
a partition for forming an inlet-side tank and an outlet-side tank by dividing a hollow portion surrounded by the header plate and the header cover front and rear;
wherein at least one of the header plate and the the header cover is a press-formed metal plate, and
wherein refrigerant flowed into the inlet-side tank is introduced into the upstream-side heat exchanging tube group, while refrigerant passing through the downstream-side heat exchanging tube group is introduced into the outlet-side tank.
In the ninth aspect of the present invention, it is possible to employ the structure that the header plate and the header cover are formed by a press-formed metal plate member, and wherein the partition is integrally formed with the header cover by folding a widthwise middle portion of the metal plate constituting the header cover along a longitudinal direction thereof, or that one of the header plate and the header cover is a press-formed metal plate, and the other thereof is an extruded molded article.
The tenth aspect of the present invention specifies a refrigerant-turn-side header member applicable to the aforementioned third or fourth aspect of the present invention.
That is, according to the tenth aspect of the present invention, a refrigerant-turn-side header member for an evaporator with a core including an upstream-side heat exchanging tube group and a downstream-side heat exchanging tube group disposed front and rear, each of heat exchanging tube group including a plurality of heat exchanging tubes arranged in parallel with each other at certain intervals, comprises:
a header plate for fixing an end portion of each of the heat exchanging tubes in a penetrated manner;
a header cover attached to the header plate so as to cover one surface side thereof; and
a partition for forming an inflow-side tank and an outflow-side tank by dividing a hollow portion surrounded by the header plate and the header cover front and rear, the partition having communication apertures for communicating with the tanks;
wherein at least one of the header plate and the the header cover is a press-formed metal plate, and
wherein refrigerant passing through the upstream-side heat exchanging tube group is introduced into the inflow-side tank and then introduced into the outflow-side tank via the communication apertures, while the refrigerant in the outflow-side tank is introduced into the downstream-side heat exchanging tube group.
In the tenth aspect of the present invention, it is possible to employ the structure that both of the header plate and the header cover are formed by a press-formed metal plate member respectively, and wherein the partition is integrally formed with the header cover by folding a widthwise middle portion of the metal plate constituting the header cover along a longitudinal direction thereof, or that one of the header plate and the header cover is a press-formed metal plate, and the other thereof is an extruded molded article.
The eleventh aspect of the present invention specifies a refrigeration system utilizing the evaporator according to the first aspect of the present invention.
According to the eleventh aspect of the present invention, a refrigeration system in which refrigerant compressed by a compressor is condensed by a condenser into a condensed refrigerant, then the condensed refrigerant is passed through a decompressing device into a decompressed refrigerant, and thereafter the decompressed refrigerant is evaporated by an evaporator and then returnes to the compressor, the evaporator comprises:
a core including an upstream-side heat exchanging tube group and a downstream-side heat exchanging tube group arranged front and rear, each of the heat exchanging tube groups including a plurality of heat exchanging tubes disposed parallel with each other at certain intervals;
an inlet-side tank disposed along one end side of the upstream-side heat exchanging tube group;
an outlet-side tank disposed along one end side of the downstream-side heat exchanging tube group; and
a refrigerant turning member disposed along the other end side of both the heat exchanging tube groups,
wherein each one end of the heat exchanging tubes constituting the upstream-side heat exchanging tube group is connected to the inlet-side tank, while the other end thereof is connected to the refrigerant turning member, and
wherein each one end of the heat exchanging tubes constituting the downstream-side heat exchanging tube group is connected to the outlet-side tank, while the other end thereof is connected to the refrigerant turning member, whereby refrigerant flowed into the inlet-side tank is introduced into the outlet-side tank via the upstream-side heat exchanging tube group, the refrigerant turning member and the downstream-side heat exchanging tube group, while the refrigerant passing through both the heat exchanging tube groups evaporates by exchanging heat with ambient air.
The twelfth aspect of the present invention specifies a refrigeration system utilizing the evaporator according to the second aspect of the present invention.
According to the twelfth aspect of the present invention, a refrigeration system in which refrigerant compressed by a compressor is condensed by a condenser into a condensed refrigerant, then the condensed refrigerant is passed through a decompressing device into a decompressed refrigerant, and thereafter the decompressed refrigerant is evaporated by an evaporator and then returns to the compressor, an evaporator, comprises:
a core including an upstream-side heat exchanging tube group and a downstream-side heat exchanging tube group arranged front and rear, each of the heat exchanging tube groups including a plurality of heat exchanging tubes disposed parallel with each other at certain intervals;
an inlet-and-outlet-side header member disposed along one end side of both the heat exchanging tube groups; and
a refrigerant-turn-side header member disposed along the other end side of both the heat exchanging tube groups,
wherein an inside of the inlet-and-outlet-side header member is divided front and rear by a partition into a front-side portion and a rear-side portion, wherein the front-side portion constitutes an inlet-side tank and the rear-side portion constitutes an outlet-side tank,
wherein one end of each of the heat exchanging tubes constituting the upstream-side heat exchanging tube group is connected to the inlet-side tank of the inlet-and-outlet-side header member, while the other end thereof is connected to the refrigerant-turn-side header member, and
wherein one end of each of the heat exchanging tubes constituting the downstream-side heat exchanging tube group is connected to the outlet-side tank of the inlet-and-outlet-side header member, while the other end thereof is connected to the refrigerant-turn-side header member,
whereby refrigerant flowed into the inlet-side tank is introduced into the outlet-side tank via the upstream-side heat exchanging tube group, the refrigerant-turn-side member and the downstream-side heat exchanging tube group, while the refrigerant passing through both the heat exchanging tube groups evaporates by exchanging heat with ambient air.
The thirteenth aspect of the present invention specifies a refrigeration system utilizing the evaporator according to the third aspect of the present invention.
According to the thirteenth aspect of the present invention, a refrigeration system in which refrigerant compressed by a compressor is condensed by a condenser into a condensed refrigerant, then the condensed refrigerant is passed through a decompressing device into a decompressed refrigerant, and thereafter the decompressed refrigerant is evaporated by an evaporator and then returns to the compressor, an evaporator, comprises:
a core including an upstream-side heat exchanging tube group and a downstream-side heat exchanging tube group arranged front and rear, each of the heat exchanging tube group including a plurality of heat exchanging tubes disposed parallel with each other at certain intervals;
an inlet-and-outlet-side header member disposed along one end side of both the heat exchanging tube groups; and
a refrigerant-turn-side header member disposed along the other end side of both the heat exchanging tube groups,
wherein an inside of the inlet-and-outlet-side header member is divided into an inlet-side tank and an outlet-side tank,
wherein the refrigerant-turn-side header member includes at least two press-formed metal plate members,
wherein an inside of the refrigerant-turn-side header member is divided into an inflow-side tank and an outflow-side tank by a refrigerant-turn-side partition, and both the tanks being communicated by communication apertures provided in the partition,
wherein one end of each of the heat exchanging tubes constituting the upstream-side heat exchanging tube group is connected to the inlet-side tank of the inlet-and-outlet-side header member, while the other end thereof is connected to the inflow-side tank of the refrigerant-turn-side header member, and
wherein one end of each of the heat exchanging tubes constituting the downstream-side heat exchanging tube group is connected to the outlet-side tank of the inlet-and-outlet-side header member, while the other end thereof is connected to the outflow-side tank of the refrigerant-turn-side header member,
whereby refrigerant flowed into the inlet-side tank is introduced into the outlet-side tank via the upstream-side heat exchanging tube group, the inflow-side tank, the apertures, the outflow-side tank and the downstream-side heat exchanging tube group, while the refrigerant passing through both the heat exchanging tube groups evaporates by exchanging heat with ambient air.
The fourteenth aspect of the present invention specifies a refrigeration system utilizing the evaporator according to the fourth aspect of the present invention.
According to the fourteenth aspect of the present invention, a refrigeration system in which refrigerant compressed by a compressor is condensed by a condenser into a condensed refrigerant, then the condensed refrigerant is passed through a decompressing device into a decompressed refrigerant, and thereafter the decompressed refrigerant is evaporated by an evaporator and then returns to the compressor, an evaporator, comprises:
a core including an upstream-side heat exchanging tube group and a downstream-side heat exchanging tube group arranged front and rear, each of the heat exchanging tube groups including a plurality of heat exchanging tubes disposed parallel with each other at certain intervals;
an inlet-and-outlet-side header member disposed along one end side of both the heat exchanging tube groups; and
a refrigerant-turn-side header member disposed along the other end side of both the heat exchanging tube groups,
wherein the inlet-and-outlet-side header member includes an inlet-and-outlet-side header plate, an inlet-and-outlet-side header cover attached to the header plate so as to cover one surface side of the header plate and a partition for dividing an inside of the inlet-and-outlet-side header member into an inlet-side tank and an outlet-side tank,
wherein the refrigerant-turn-side header member includes a refrigerant-turn-side header plate and a refrigerant-turn-side header cover attached to the header plate so as to cover one surface side of the header plate, one of the refrigerant-turn-side header plate and the refrigerant-turn-side header cover being formed by a press-formed metal plate member, and the other thereof being formed by an extruded molded article,
wherein one end of each of the heat exchanging tubes constituting the upstream-side heat exchanging tube group is fixed to the inlet-and-outlet-side header plate in a penetrated manner to thereby be connected to the inlet-side tank, while the other end thereof is connected to the refrigerant-turn-side header plate in a penetrated manner,
wherein one end of each of the heat exchanging tubes constituting the downstream-side heat exchanging tube group is fixed to the inlet-and-outlet-side header member to thereby be connected to the outlet-side tank, while the other end thereof is connected to the refrigerant-turn-side header member in a predetermined manner,
whereby refrigerant flowed into the inlet-side tank is introduced into the outlet-side tank via the upstream-side heat exchanging tube group, the refrigerant-turn-side header member and the downstream-side heat exchanging tube group, while the refrigerant passing through both the heat exchanging tube groups evaporates by exchanging heat with ambient air.
The core 1 is provided with a plurality of flat tubular elements 5 and a plurality of corrugated fins 2.
As shown in
Each heat exchanging tube 6 and 7 is provided with a plurality of heat exchanging passages 6a and 7a arranged in parallel each other and extending along the longitudinal direction thereof (i.e., the direction of extrusion). On the inner peripheral surface of each heat exchanging passage 6a and 7a, inwardly protruded inner fins 6b or 7b are integrally formed.
The core 1 is formed by alternatively laminating the aforementioned tubular members 5 and corrugated fins 2 in the core width direction and disposing a side plate 3 on the external side of the respective outermost corrugated fin 2. Thus, each heat exchanging tube 6 located at the upstream-side among the plurality of tubular members 5 form an upstream-side heat exchanging tube group as a first pass P1, while each heat exchanging tube 7 located at the downstream-side form a downstream-side heat exchanging tube group as a second pass P2.
In this embodiment, it is preferable that the tube height H is set to 0.75 to 1.5 mm. The lower limit of the tube height H is preferably set to 1.0 mm or more.
Furthermore, it is preferable that each width of the heat exchanging tube 6 and 7 is set to 12 to 18 mm. As for the tubular member 5 integrally provided with the tubes 6 and 7, the width is preferably set to 32 to 38 mm. Furthermore, as for the wall thickness of the peripheral wall of the tube 6 and 7, it is preferable that the wall thickness is set to 0.175 to 0.275 mm. Furthermore, as for the wall thickness of the partitioning wall for dividing the heat exchanging passage 6a and 7a in the tube 6 and 7, it is preferable that the wall thickness is set to 0.175 to 0.275 mm, while the pitch of the partitioning wall is preferably set to 0.5 to 3.0 mm. Furthermore, as for the radius of curvature R of the external side surface of the side portion of the heat exchanging tube 6 and 7, it is preferable to set to 0.35 to 0.75 mm.
Furthermore, the height (fin height) of the corrugated fin 2 is preferably set to 7.0 to 10 mm, and the pitch (fin pitch) of the fin 2 is preferably set to 1.3 to 1.8 mm.
That is, in cases where the structure falling within the numerical scope is employed, good heat exchange performance can be obtained.
In this embodiment, although heat exchanging tubes 6 and 7 are integrally formed, the present invention is not limited to it. The present invention allows forming both the tubes 6 and 7 separately. Furthermore, the heat exchanging tube 6 and 7 is not limited to an extruded molded article. For example, the heat exchanging tube 6 and 7 may be a bend-formed article having inner fins obtained by bending a plate member or a roll-formed article having a heat exchanging passage obtained by rolling a plate member.
Furthermore, in this invention, a plate fin may be used in place of the corrugated fin 2.
As shown in
At the front-half region and the rear-half region of the header plate 20, a plurality of tube mounting apertures 21 are formed at certain intervals along the longitudinal direction, respectively.
The header cover 30 is disposed so as to cover the upper surface side of the header plate 20 from the above. At the middle position of the lower surface in the fore-and-aft direction, a partitioning wall 31 is integrally formed so as to extend along the longitudinal direction (the core width direction).
By the space surrounded by the header plate 20 and the header cover 30 and positioned in front of the partitioning wall 31, an outlet-side tank 12 having a tube shape and extending in the core width direction is formed. On the other hand, by the space surrounded by the header plate 20 and the header cover 30 and positioned behind the partitioning wall 31, an inlet-side tank 11 having a tube shape and extending in the core width direction is formed.
Furthermore, a refrigerant inlet 11a is formed at the longitudinal middle portion of the header cover 30 of the inlet-side tank 11, while a refrigerant outlet 12a is formed at the portion of the header cover 30 of the outlet-side tank 12.
Furthermore, in the inlet-side tank 11, a refrigerant distributing resistance plate 41 is provided so as to divide the inner space into an upper space and a lower space. This refrigerant distributing resistance plate 41 is equipped with a plurality of refrigerant passage apertures 41a formed at certain intervals in the longitudinal direction. In the refrigerant passage apertures 41a, the diameter of the aperture 41a near the refrigerant inlet 11a, or the diameter of the aperture 41a located at the longitudinal central portion, is formed to be the smallest, while the diameters of the other apertures 41a are formed to become gradually larger as it goes toward the longitudinal end portion from the longitudinal central portion.
In the outlet-side tank 12, an uneven-distribution-flow preventing resistance plate 42 is provided so as to divide the inside space into an upper space and a lower space. This uneven-distribution-flow preventing resistance plate 42 is provided with a plurality of refrigerant passage apertures 42a, which are the same in diameter, at certain intervals along the longitudinal direction.
Furthermore, as shown in
Furthermore, to the refrigerant inlet 11a and the refrigerant outlet 12a of the upper header member 10, joint tubes 11b and 12b are fixed so as to communicate with the inlet 11a and outlet 12a.
In this embodiment, the refrigerant distributing resistance plate 41 and the uneven-distribution-flow preventing resistance plate 42 are formed separately to the header plate 20 and the header cover 30. In the present invention, however, these resistance plates 41 and 42 may be integrally formed with the header plate 20 and/or the header cover 30. Furthermore, the partitioning wall 31 may be integrally formed with the header plate 20. Alternatively, the partitioning wall 31 may be formed as a separate member.
To each of the tube mounting apertures 21 of the header plate 20 constituting the aforementioned upper header member 10, the upper end of each of the heat exchanging tubes 6 and 7 constituting the aforementioned core 1 is fixed in an inserted state. In this state, the upstream-side heat exchanging tubes 6 are communicated with the inlet-side tank 11, while the downstream-side heat exchanging tubes 7 are communicated with the outlet-side tank 12.
On the other hand, as shown in
The header plate 60 is provided with a plurality of tube mounting apertures 61 arranged at certain intervals in the longitudinal direction thereof at the front half region and the rear half region thereof respectively.
The header cover 70 is attached to the header plate 60 so as to cover the lower surface of the header plate, and has, at the widthwise middle position on the upper surface thereof, a partitioning wall 71 continuously extending in the longitudinal direction of the header cover (the core width direction). This partitioning wall 71 is provided with a plurality of cut-out communication apertures 71a at certain intervals in the longitudinal direction.
By the space surrounded by the header plate 60 and the header cover 70 and positioned behind the partitioning wall 71, an inflow-side tank 51 having a tube shape and extending in the core width direction is formed. On the other hand, by the space surrounded by the header plate 60 and the header cover 70 and positioned in front of the partitioning wall 71, an outflow-side tank 52 having a tube shape and extending in the core width direction is formed. In this case, the inflow-side tank 51 and the outflow-side tank 52 are communicated by the cut-out communication apertures 71a formed in the partitioning wall 71.
Furthermore, as shown in
To each of the tube mounting apertures 51 of the header plate 60 of the aforementioned lower header member 50, the lower end of each heat exchanging tube 6 and 7 is fixed in an inserted manner. In this state, the upstream-side heat exchanging tube 6 is communicated with the inflow-side tank 51 of the lower header member 50, while the downstream-side heat exchanging tube 7 is communicated with the outflow-side tank 52.
In the evaporator of the first embodiment constituted as mentioned above, each component is made of aluminum or its alloy, or an aluminum brazing sheet in which a brazing layer is laminated on at least one surface of the brazing sheet. These components are provisionally assembled together with brazing materials if necessary into a predetermined evaporator configuration. Then, this provisionally assembled product is collectively brazed in a furnace to integrally connect the components.
In this invention, however, the method of connecting the components is not specifically limited and may be performed by any known procedure.
The aforementioned evaporator is mounted as an automobile refrigeration cycle together with a compressor, a condenser and decompressing means such that the front-face side (the downstream-side heat exchanging tube group side P2) and the rear-face side (the upstream-side heat exchanging tube side P1) constitute an air taking-in side and an air taking-out side, respectively.
Then, the mist-like two phase refrigerant including a liquid phase and a vapor phase passed the compressor, the condenser and the decompressing means is introduced into the inlet-side tank 11 of the upper header member 10 via the refrigerant inlet 11a of the aforementioned evaporator.
The refrigerant introduced into the inlet-side tank 11 is distributed by the refrigerant distributing resistance plate 41 in the longitudinal direction of the tank 11 and passes through each refrigerant passage aperture 41a of the resistance plate 41. At this time, the refrigerant tends to pass through the refrigerant passage apertures 41a near the refrigerant inlet 11a, i.e., the refrigerant passage apertures 41a located at the longitudinal middle portion, at a large rate because of the inertia. However, in this embodiment, since the flow velocity of the refrigerant decreases by the resistance plate 41, the refrigerant distributes smoothly in the longitudinal direction and passes through each refrigerant passage aperture 41a. Furthermore, in this embodiment, the refrigerant passage aperture 41a of the resistance plate 41 is formed to be small in diameter at the longitudinal middle portion, while the refrigerant passage aperture 41a is formed to be larger as it goes toward the end portion of the resistance plate 41. Therefore, the volume of refrigerant passing through each refrigerant passage aperture 41a is restricted moderately, and therefore the refrigerant equally passes through each refrigerant passage aperture 41a. This also enables to effectively distribute the refrigerant in the longitudinal direction of the inlet-side tank 10.
The refrigerant equally distributed by the resistance plate 41 is equally introduced into each tube 6 of the upstream-side heat exchanging tube group P1.
The refrigerant introduced into the upstream-side heat exchanging tube group P1 is introduced into the inflow-side tank 51 of the lower header member 50 through each tube 6, and then introduced into the outflow-side tank 52 through the cut-out communication apertures 71a of the partitioning wall 71.
Since the refrigerant passing through the upstream-side heat exchanging tube group P1 is equally distributed into each heat exchanging tube 6, the refrigerant is equally distributed and introduced into each tube 7 of the downstream-side heat exchanging tube group P2 by passing through the inflow-side tank 51 and the outflow-side tank 52s of the lower header member 50 while keeping the equally distribution state.
The refrigerant passed through each downstream-side heat exchanging tube 7 is introduced into the outlet-side tank 12 of the upper header member 10. In the outlet-side tank 12, the refrigerant receives a moderate flow resistance by the uneven-distribution-flow preventing resistance plate 42, resulting in an equally balanced pressure of refrigerant at the entire longitudinal direction of the outlet-side tank 12, which assuredly prevents uneven-distribution-flow of the refrigerant. Thus, the refrigerant flows out of the refrigerant outlet 12a via each refrigerant passage aperture 42a of the resistance plate 42.
Since the uneven-distribution-flow preventing resistance plate 42 prevents the refrigerant from being unevenly distributed in the outlet-side tank 12, the refrigerant is effectively prevented from being unevenly distributed in the downstream-side heat exchanging tube group P2. Thus, the refrigerant can pass through each heat exchanging tube 7 at the downstream-side in an evenly distributed manner.
The refrigerant flowed out of the refrigerant outlet 12a of the upper header member 10 is returned to the compressor in the aforementioned refrigeration cycle.
The refrigerant passing through the upstream and downstream-side heat exchanging tube groups P1 and P2 absorbs heat from the air A taken from the front-side of the core 1 and evaporates by exchanging heat with the air. Furthermore, the air A cooled by the heat absorption flows out of the rear-side of the core 1, and is sent to the interior of a car.
As mentioned above, according to the evaporator of this embodiment, the refrigerant passes through each heat exchanging tube 6 and 7 of the upstream-side and downstream-side heat exchanging tube groups P1 and P2 in an equally distributed manner. Therefore, the refrigerant can exchange heat at the entire region of the heat exchanging tube groups P1 and P2, i.e., the entire region of the core 1, resulting in an improved heat exchange performance.
Furthermore, in this embodiment, since the refrigerant passes through two tube groups P1 and P2 forming a simple U-shaped refrigerant passage, the refrigerant flow resistance can be decreased. As a result, the passage cross-sectional area of the refrigerant can be decreased, and therefore the tube height of each heat exchanging tube 6 and 7 can be decreased. Accordingly, the size, weight and thickness can be further decreased. Furthermore, by decreasing the tube height, the installation number of heat exchanging tubes 6 and 7 can be increased without changing the evaporator size, resulting in further enhanced refrigeration dispersibility, which in turn can further improve the heat exchange performance.
Furthermore, in the present embodiment, the partitioning wall 31 disposed between the upper wall and the bottom wall of the upper header member 10 continuously extends within the upper header member 10 in the longitudinal direction, and the partitioning wall 71 disposed between the upper wall and the bottom wall of the lower header member 50 continuously extends within the lower header member 50 in the longitudinal direction. Accordingly, these partitioning walls 31 and 71 reinforce each header member 10 and 50, and therefore both the header members 10 and 50 can be improved in pressure resistance.
Furthermore, in this embodiment, a tubular member 5 which is formed by integrally connecting the corresponding heat exchanging tubes 6 and 7 of the upstream-side heat exchanging tube group P1 and the downstream-side heat exchanging tube group P2 is employed. Therefore, the upstream-side and downstream-side heat exchanging tubes 6 and 7 can be formed by simply laminating the aforementioned tubular members 5. As a result, the evaporator can be fabricated easily. Furthermore, since the heat exchanging tubes 6 and 7 are connected between the heat exchanging tube groups P1 and P2, the strength of the assembly is increased.
Now, in the evaporator according to this embodiment, the relation of the tube height H of the heat exchanging tube and the heat exchanging amount ratio % is shown in
By the way, in a conventional heat exchanging tube used for the so-called header type heat exchanger, it is considered that the tube height preferably falls within the range of about 1.5 to 3.0 mm which is twice the height of the tube height of the evaporator according to this embodiment.
Furthermore, in the aforementioned embodiment, although the refrigerant distributing resistance plate 41 and the uneven-distribution-flow preventing resistance plate 42 are provided in the inlet-side tank 11 and the outlet-side tank 12 of the upper header member 10, the present invention is not limited to it. For example, as shown in
Furthermore, in the aforementioned embodiment, although the refrigerant inlet 11a and outlet 12a are formed in the longitudinal middle upper portion of the upper header member 10, the present invention is not limited to it. For example, as shown in
Furthermore, in the aforementioned embodiment, as shown in
Furthermore, in the aforementioned embodiment, as shown in
Furthermore, in the evaporator of the aforementioned embodiment, although an air A is introduced from the downstream-side heat exchanging tube group P2 as an evaporator front side, the present invention is not limited to it. In the present invention, an air A may be introduced from the upstream-side heat exchanging tube group P1 as an evaporator front side.
Furthermore, in this embodiment, the installation direction of the evaporator is not limited to a specific direction, and the evaporator may be installed at any direction.
That is, as shown in
As shown in
This header cover 30 is fixed to the header plate 20 in a state that the header cover 30 covers the upper surface side of the header plate 20 and the tip of the engaging protrusion 32 of the partitioning wall 31 is inserted in the engaging aperture 22 of the header plate 20 and caulked.
In this state, at the front-side space of the partitioning wall 31 surrounded by the header plate 20 and the header cover 30, an outlet-side tank 12 of a tube shape extending in the core width direction is formed, while at the rear-side space of the partitioning wall 31 an inlet-side tank 11 of a tube shape extending in the core width direction is formed.
As shown in
As shown in
This header cover 70 is fixed to the header plate 60 in a state that the header cover 70 covers the lower surface side of the header plate 60 and the tip of the engaging protrusion 72 of the partitioning wall 71 is inserted in the engaging aperture 62 of the header plate 60 and caulked. In this state, at the rear-side space of the partitioning wall 71 surrounded by the header plate 60 and the header cover 70, an inflow-side tank 51 of a tube shape extending in the core width direction is formed, while at the front-side space of the partitioning wall 71 an outflow-side tank 11 of a tube shape extending in the core width direction is formed. Furthermore, the inflow-side tank 51 and the outflow-side tank 52 are communicated with each other via communication apertures 71a formed in the partition 71.
Then, as shown in
Since the other structure is essentially the same as in the first embodiment, the duplicate explanation will be omitted by allotting the same reference numeral to the same or corresponding portion.
In this evaporator of the second embodiment, in the same manner as in the first embodiment, the evaporator components are provisionally assembled into a predetermined evaporator configuration, and the provisionally assembled product is collectively brazed in a furnace to thereby integrally connect them.
According to the evaporator of this second embodiment, the same effects as in the first embodiment can be obtained.
Moreover, since an aluminum press-formed plate member is used as the structural member 20, 30, 60 and 70 of each header member 10 and 50, the header structural member 20, 30, 60 and 70 can be continuously manufactured from a coiled aluminum member, resulting in an enhanced productivity.
Furthermore, since the header structure member 20, 30, 60 and 70 is made of a plate member, a brazing sheet having clad materials such as brazing materials or sacrifice materials laminated on at least one side surface thereof can be used as the header structure member 20, 30, 60 and 70, resulting in an enhanced brazability. Especially, in cases where cladding materials are laminated on the external surface side, the corrosion protection nature can be improved by containing zinc (Zn) into the cladding materials to thereby form a sacrifice material layer.
Furthermore, since the partitioning wall 31 and 71 of both the header members 10 and 50, sufficient strength can be secured while decreasing the header height and the wall thickness, resulting in a reduced size and weight. Especially, since the partitioning wall 31 and 71 is formed by folding a plate member, sufficient strength can be secured even if the thickness is thin, which enables to further decrease the size and weight.
In the second embodiment, the refrigerant distributing resistance plate 0.41 and the uneven-distribution-flow preventing resistance plate 42 may be provided in the header member 10 and 50 in the same manner as in the first embodiment.
Furthermore, in this embodiment, although the header plate 20 and 60 and the header cover 30 and 70 constituting the header member 10 and 50 are formed by an aluminum plate respectively, in the present invention, a part of these members may be made of an extruded molded article.
In cases where an extruded molded article is used as a part of header structure member, it is difficult to form a sacrifice layer by itself. Therefore, before subjecting it to collective brazing processing, a flux containing zinc is applied to the extruded molded article. This enables to form a zinc diffusion layer (sacrifice layer) on the external surface, resulting an improved corrosion resistance.
Furthermore, in the second embodiment too, in the same manner as in the first embodiment, the position of the refrigerant inlet and/or the refrigerant outlet, the air take-in direction and the installation direction of the evaporator are not specifically limited.
As mentioned above, according to the first to fourth aspect of the present invention, since the refrigerant passage is formed into a simple U-shape, the refrigerant flow resistance can be decreased. As a result, the refrigerant flow cross-sectional area can be decreased and the tube height of the heat exchanging tube can be decreased. Accordingly, the size, weight and thickness of the evaporator can be reduced. Furthermore, in cases where the tube height is decreased, the number of tubes can be increased without increasing the core size. Therefore, the refrigerant dispersibility can be improved, resulting in improved heat exchanging performance. Especially, according to the evaporator of the third and fourth aspect of the present invention, since the header member is made of a metal press-formed plate, the productivity can be improved and the brazability and corrosion resistance can also be improved by using a brazing sheet.
The fifth to eighth aspect of the present invention specify a manufacturing process of the evaporator of the first to fourth aspect of the present invention. Therefore, the aforementioned evaporator can be manufactured more assuredly.
Furthermore, the ninth and tenth aspects of the present invention specify a header member applicable to the evaporator of the third or fourth aspect of the present invention. Therefore, the aforementioned evaporator can be manufactured more assuredly.
The eleventh to fourteenth aspects of the present invention specify a refrigerant system using the evaporator of the first to fourth aspect of the present invention. Therefore, the aforementioned effects can be obtained more assuredly.
The terms and expressions which have been employed herein are used as terms of description and not of limitation, and there is no intent, in the use of such terms and expressions, of excluding any of the equivalents of the features shown and described or portions thereof, but it is recognized that various modifications are possible within the scope of the invention claimed.
As mentioned above, the evaporator, the manufacturing method thereof, the header member for evaporators and a refrigeration system can improve heat exchanging performance while reducing the size and weight. Therefore, they can be preferably used for a refrigeration cycle for car air-conditioning system especially.
| Number | Date | Country | Kind |
|---|---|---|---|
| 2001-183062 | Jun 2001 | JP | national |
This application is an application filed under 35 U.S.C. §111(a) claiming the benefit pursuant to 35 U.S.C. §119(e)(1) of the filing date of Provisional Application No. 60/303,145 filed on Jul. 6, 2001 pursuant to 35 U.S.C. §111(b).
| Filing Document | Filing Date | Country | Kind | 371c Date |
|---|---|---|---|---|
| PCT/JP02/06046 | 6/17/2002 | WO | 00 | 12/18/2003 |
| Publishing Document | Publishing Date | Country | Kind |
|---|---|---|---|
| WO02/103263 | 12/27/2002 | WO | A |
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|---|---|---|---|
| 5205347 | Hughes | Apr 1993 | A |
| 5761808 | Patel et al. | Jun 1998 | A |
| 5934367 | Shimmura et al. | Aug 1999 | A |
| 6189604 | Yamauchi et al. | Feb 2001 | B1 |
| 6615588 | Hoecker | Sep 2003 | B1 |
| Number | Date | Country |
|---|---|---|
| 5-296606 | Nov 1993 | JP |
| 9-166368 | Jun 1997 | JP |
| 11-94398 | Apr 1999 | JP |
| 11-337293 | Dec 1999 | JP |
| 2000-203250 | Jul 2000 | JP |
| 2001-66018 | Mar 2001 | JP |
| Number | Date | Country | |
|---|---|---|---|
| 20040159121 A1 | Aug 2004 | US |
| Number | Date | Country | |
|---|---|---|---|
| 60303145 | Jul 2001 | US |
