• 专利附录
  • 专利说明
  • 权利要求
  • 类似技术
  • 同族专利
  • 引用文献
  • 法律状态
  • 优先权
    • 专利摘要:
    The invention relates to a heat exchanger comprising a plurality of stacked plates 3 intended to allow a heat exchange between a first fluid and a second fluid flowing in contact with said plates 3, said exchanger comprising a bottle 11 for the first fluid, said plates 3 being provided with intermediate orifices 69b, 75 allowing a circulation of the first fluid between said plates 3 and said bottle 11, said intermediate orifices 69b, 75 being arranged along a direction substantially transverse to a principal direction of longitudinal extension of each plate 3.
    公开号:FR3035488A1
    申请号:FR1553779
    申请日:2015-04-27
    公开日:2016-10-28
    发明作者:Jerome Mougnier；Gael Durbecq
    申请人:Valeo Systemes Thermiques SAS；
    IPC主号:
    专利说明:

    [0001] The present invention relates to a stacked plate heat exchanger, in particular a condenser for exchanging heat between a refrigerant and a cooling fluid in the liquid phase. BACKGROUND OF THE INVENTION
    [0002] In this field, it is known heat exchangers comprising a heat exchange bundle having a series of plates stacked parallel to one another above. The stack of plates forms heat exchange surfaces, between which a refrigerant and a cooling fluid circulate, in alternating layers, in fluid passage circuits. The stack of plates is thus configured to define two different circuits: that of the refrigerant and that of the cooling fluid. Among these exchangers, there are exchangers further provided with a bottle for the refrigerant and a subcooling portion, located downstream of the bottle. In this case, the stacked plates are separated into two parts including a cooling part and a subcooling part and are provided with at least two refrigerant circulation ports in communication with the bottle. It is known to arrange these orifices along a direction parallel to a direction of longitudinal extension of said stacked plates. This positioning of the circulation orifices nevertheless has the disadvantage of creating on the surface of said plates areas where the flow of the refrigerant, and therefore the heat exchange between the refrigerant and the cooling fluid, is low or even zero. One of the objectives of the invention is to solve the problem explained above by proposing a heat exchanger comprising a plurality of stacked plates intended to allow a heat exchange between a first fluid and a second fluid flowing in contact with said plates. , said exchanger comprising a bottle for the first fluid, said plates being provided with intermediate orifices permitting a circulation of the first fluid between said plates and said bottle, said intermediate orifices being arranged along a direction substantially transverse to a direction main longitudinal extension of the plates. In this way, the flow direction of said refrigerant being transverse to the direction in which the intermediate orifices are aligned, the areas of low heat exchange are limited. According to various embodiments, which may be taken together or separately: said plates are configured to define each two parts, a first part of which allows heat exchange between the first fluid and the second fluid before the first fluid passes into the first fluid; bottle and a second part to allow a heat exchange between the first fluid and the second fluid after passage of the first fluid in the bottle, said intermediate orifices being arranged between said first and second parts, - said first parts of the plates define a zone of condensation and said second portions define a subcooling zone, a first one of said intermediate ports allows circulation of the first fluid from the condensation zone to the bottle, a second of said intermediate ports, allowing circulation of the first fluid of the bottle to the zone of subcooling, the plates further comprise an additional orifice, said circulation in passes, aligned with the first and second intermediate orifices, the circulation orifice in passes of at least one of the plates, said secondary plate. , is obstructed so as to allow the circulation of said first fluid in several passes in the condensation zone, - the bottle extends in said main direction of the plates 3035488 3 - said heat exchanger being provided with inlet pipes and tubings outlet, said bottle and said manifolds are located on the same side of the heat exchanger, said upper side, - said intermediate orifices, have an oblong shape and / or elongated in a direction of flow of said second fluid, - each of said intermediate orifices has a width, measured in a direction transverse to said main direction of longitudinal extension ale, which decreases over almost the entire length of the orifice in a direction of flow of said second fluid. The invention will be better understood, and other objects, details, features and advantages thereof will become more clearly apparent from the following detailed explanatory description of at least one embodiment of the given invention. by way of purely illustrative and non-limiting example, with reference to the accompanying schematic drawings: - Figure 1 is a side view of a heat exchanger according to the invention. FIG. 2 is a view, according to section A-A, of a heat exchanger according to the invention, in a first embodiment. FIG. 3 is a view, according to section A-A, of a heat exchanger according to the invention, in a second embodiment. - Figure 4 is a perspective view of a portion of the front of a first type of plates according to the invention, in the first embodiment. FIG. 5 is a perspective view of a part of the front of a second type of plate according to the invention, in the first embodiment. - Figure 6 is a perspective view of a portion of the front of a third type of plates according to the invention, in the first embodiment. - Figure 7 is a perspective view of a portion of the front of a fourth type of plates 25 according to the invention provided with a partition. FIG. 8 is a perspective view of the front of the second type of plates according to the invention, in the first embodiment. - Figure 9 is a perspective view of the front of the fourth type of plates, in the first embodiment. FIG. 10 is a perspective view of a first type of plate according to the invention, in the second embodiment. - Figure 11 is a perspective view of a portion of the front of a second type of plates according to the invention, in the second embodiment. The invention relates to a heat exchanger between a first and a second fluid, in particular a condenser of an air conditioning circuit, more particularly in a motor vehicle. Said first fluid is for example a refrigerant, such as the fluid known as R134a or the one known as R1234yf. The heat exchanger is configured so that said first fluid enters the gas phase and comes out of the liquid phase. The second fluid is for example a coolant which may be water mixed with an antifreeze agent such as glycol. In other words, the coolant may be a mixture of water and glycol. As illustrated in FIGS. 2 and 3, said exchanger comprises a bundle 1 of stacked plates 3 along a stacking direction 5 so as to define passages 7, 9 for said first fluid and said second fluid, said fluids exchanging heat with each other. Advantageously, the same plate 3 defines with another plate 3 adjacent a passage 7 for the first fluid and defines with another adjacent plate 3 a passage 9 for the second fluid. In other words, the passages 7 for the first fluid and the passages 9 for the second fluid alternate alternately. Said beam 1 here has a parallelepiped shape.
    [0003] In other words, said stacked plates 3 are designed so as to define between them a first circuit for the circulation of the first fluid and a second circuit for the circulation of the second fluid, said circuits being designed to allow a circulation of the first fluid avoiding the second circuit and a circulation of the second fluid avoiding the first circuit. Said first and second circuits respectively comprise the passages 7 for the first fluid and the passages 9 for the second fluid. As illustrated in Figure 1, said exchanger further comprises a bottle 11 for said first fluid. In the case of a condenser, said bottle 11 is designed to separate the gaseous and liquid phases of said refrigerant so that only the liquid phase is allowed to flow downstream of the bottle 11. Said bottle 11 may also comprise a filter and / or a desiccator so as to filter and / or dry said first fluid. Said plates 3 each comprise two parts 130, 150 including a first portion 130 designed to allow a heat exchange between the first fluid and the second fluid before the first fluid passes into the bottle 11 and a second portion 150 designed to allow an exchange of heat between the first fluid and the second fluid after passage of the first fluid in the bottle 11. Said first 130 and second 150 parts of the plates 3 define in the beam respectively a first zone 13 and a second zone 15. In the case of a condenser, said first zone 13 is a condensation zone and said first zone 15 is a sub-cooling zone. It is noted that the beam 1 is configured so that the first fluid can not flow directly between the passages for the first fluid 7 of the first zone 13 and those of the second zone 15. As illustrated in FIGS. 8 and 9, said plates stacked 3 are for example of rectangular shape. Said plates 3 each comprise a lower edge 31 and an upper edge 32 and advantageously extend in a principal direction of longitudinal extension between said edges 31, 32, said longitudinal extension direction advantageously being parallel to a direction of direction. longitudinal extension of the bottle. Said lower 31 and upper 32 edges are opposed to each other along said longitudinal extension main direction. Said plates 3 also comprise two longitudinal edges 34 which extend longitudinally 5 between said lower edge 31 and said upper edge 32. Said plates 3 also comprise, at their periphery, a raised edge 30. The plates 3 are designed to be arranged in contact each other, for example brazed, at said raised edges 30. Said plates 3 have two faces including a front and back, said raised edge 30 being arranged on said front of each plate 3. In other words, said raised edge 30 protrudes from the side of the front of each of the plates 3.
    [0004] Said plates 3 are for example obtained by stamping, perforating and / or molding a laminated metal plate, for example aluminum or and / or an aluminum alloy. With regard to said first fluid, said bottle 11 is connected upstream with said first zone 13 of the beam 1 and downstream with said second zone 15 of the beam 1. In other words, said heat exchanger is configured so that said first fluid 15 flows successively through said first zone 13 of the bundle 1, said bottle 11 and said second zone 15 of the bundle 1. Said heat exchanger comprises an inlet inlet pipe for the first fluid 19i, an outlet pipe for the first fluid 190, an inlet manifold 18i for the second fluid and an outlet pipe 180 for the second fluid.
    [0005] As illustrated in FIG. 1, advantageously, said tubings and the bottle 11 are arranged on the same side of the heat exchanger. Here, said inlet and outlet pipes are situated on an upper side 17, for example near opposite corners of said upper side 17.
    [0006] Advantageously, the heat exchanger is configured such that said first fluid enters the beam 1 through said inlet pipe for the first fluid 19i. Said first fluid then flows through the first zone 13, then flows through the bottle 11 and returns to the beam 1 where it flows through the second zone 15. Said first fluid finally leaves 5 of said beam 1 through the outlet pipe for the first fluid 190. Advantageously, unlike the first fluid, said beam 1 is configured so that said second fluid flows in the beam 1 directly from one to the other of said first fluid. 130 and second 150 zones without passing through the bottle 11. Here, the direction of flow of the second fluid is substantially the same in the entirety of the beam 1.
    [0007] The bottle 11 advantageously extends parallel to said upper side 17 of the bundle 1. Said bottle 11 is located here between said manifolds 19i, 190. Accordingly, depending on the length available for the bottle 11, the cross-section of the bottle It is adapted to obtain the desired volume. With this ability to vary the volume of the bottle 11 by varying the cross section thereof, the tubings 19i, 190 are more easily accessible. This configuration allows a high level of integration and the use of a bottle 11 easy to manufacture. Said heat exchanger may also, for example, comprise a reinforcing plate 49 on said upper side 17. As illustrated in FIG. 2, said bundle 1 advantageously defines several passes, here three passes 25a, 25b, 25c, for said first fluid in said first zone 13. Said passes 25a, 25b, 25c, are configured so that said first fluid flows successively from one pass to another in this order by changing direction between each pass. Such circulation of the first fluid makes it possible to increase the heat exchange while limiting the pressure drops, in particular when the number of passages associated with each pass decreases from one pass to the other along the flow of the first fluid, in the case where said first zone 13 is for example a condensation zone for the first fluid. Advantageously, the number of said passes 25a, 25b, 25c is odd to optimize the relative location of the bottle 11 and the inlet of the first fluid 19i.
    [0008] Said heat exchanger here comprises manifolds for the first fluid configured to allow said first fluid to flow from one of said passages 7 for the first fluid to the next passage 7 for the first fluid, this avoiding the circuit for the second fluid. fluid. Similarly, said exchanger 1 is provided with manifolds for the second fluid configured to allow said second fluid to flow from one of said passages 9 for the second fluid to the next passage 9 10 for the second fluid, this avoiding the circuit for the first fluid. Said collectors are defined by orifices provided with said plates 3. Each collector is arranged through the plates 3. In particular, each collector advantageously has a principal direction of longitudinal extension parallel to the stacking direction 5 of the plates 3. In other words, said collectors are arranged parallel to the stacking direction 5 of the plates 3. More precisely, said beam 1 comprises a collector for the entry of the first fluid into the first zone 13, called the main inlet manifold 51a. said main inlet manifold 51a being connected to the inlet manifold 19i of the first fluid. Said beam 1 also comprises a collector for the outlet of the first fluid from the first zone 13, said first intermediate manifold 55, connected to the bottle 11. Said beam 1 20 further comprises a manifold for the entry of the second fluid into the first zone 13 connected to the inlet pipe 18i of the second fluid. Said beam 1 further comprises a manifold for the entry of the first fluid in the second zone 15 from the bottle 11, said second intermediate manifold 51b, connected to the bottle 11. Said beam 1 also comprises a manifold 51c for the output of the first fluid of the second zone 15, said main outlet manifold 51c, connected to the outlet pipe 190 of the first fluid. Said beam 1 further comprises an outlet manifold of the second fluid connected to the outlet pipe 180 of the second fluid. The first 55 and second intermediate collectors 51b are arranged in the beam 1 between the first 13 and second 15 zones.
    [0009] The main inlet manifold 51a, the main outlet manifold 51c, the inlet manifold of the second fluid in the first zone and the outlet manifold of the first fluid of the second zone are all arranged along side edges 18 of the first zone. beam 1, parallel to the stacking direction 5 of the plates 3. It will be noted that the main inlet manifold 51a is connected both to the inlet pipe 19i for the first fluid and to each of the passages 7 for the first fluid. first fluid in the first zone 13 of the beam 1. The main outlet manifold 51c is connected both to the outlet pipe 190 for the first fluid and to each of the passages 7 for the first fluid to the inside of the second zone 15. It will also be noted that the first intermediate manifold 55 allows the flow of the first fluid from the first zone 13 of the bundle 1 to the bottle 11. The second intermediate manifold 51b allows it, the flow of the first fluid from the bottle 11 to each of the passages 7 for the first fluid in the second zone 15 of the beam 1. As illustrated in Figure 2, in the case of a multiple pass exchanger, said beam 1 further comprises a third intermediate manifold 53 for the circulation of the first fluid in several passes. Said third intermediate manifold 53 is designed to allow a direct flow of the first fluid between said third intermediate manifold 53 and each of the passages 7 for the first fluid inside the first zone 13.
    [0010] The first, second and third intermediate collectors 55, 51b, 53 are then arranged in the bundle 1 between the first zone 13 and the second zone 15, parallel to each other. Advantageously, in order to allow the circulation of the first fluid in several passes in the first zone 13, more precisely here in three passes, the main inlet manifold 51a and the intermediate manifold 53 each comprise a partition 57. separation 57 are for example planar walls arranged in said collectors transversely to the main direction of longitudinal extension of said collector. Said partition walls 57 are arranged to separate an interior space of said manifold into longitudinal portions opposite to each other along the main direction of longitudinal extension of said manifold. Said partition walls 57 are configured to limit or even prevent the flow of the first fluid between said two parts of a collector, said parts being separated from each other by said partition wall 57. Said partition walls 57 are arranged in each manifold 51a, 53 for generating said circulation in a plurality of passes 25a, 25b, 25c, by shifting, in the stacking direction, between the location of one of the partition walls 57 in said main manifold of inlet 51a and the location of another partition wall 57 in the third intermediate manifold 53. Each partition wall 57 is configured to change the flow direction of said first fluid in the first zone 13 of the beam 1.
    [0011] As illustrated in FIGS. 4 to 9, the plates 3 each comprise a plurality of orifices, each of the orifices corresponding to one of the collectors of the beam 1. It should be noted that said orifices are arranged identically on each plate 3 so that, when of the stacking of the plates 3 on each other, the superposition of said orifices of each plate 3 defines each of the collectors of the beam 1.
    [0012] In particular, said plates 3 comprise a first intermediate orifice 75 and a second intermediate orifice 69b both allowing a circulation of the first fluid between said plates 3 and said bottle 11. Said first intermediate orifice 75 corresponds to the manifold 55 while said second intermediate orifice 69b corresponds to the collector 51b.
    [0013] According to the invention, said first and second intermediate orifices 69b and 75 are aligned along a substantially transverse direction and / or orthogonal to the main direction of longitudinal extension of the plates 3. In other words, said first and second orifices 69b and 75 are centered on a line substantially transverse and / or orthogonal to the general direction and / or average flow of the first fluid.
    [0014] In the case of a multi-pass heat exchanger, the plates 3 further comprise an additional orifice 73, said third intermediate orifice 73, said third intermediate orifice 73 allowing circulation in passes and being aligned with said first 75 and second 69b intermediate ports. Said third intermediate orifice 73 corresponds here to the third intermediate manifold 53.
    [0015] The alignment of said intermediate orifices 69b, 75, 73 along a same line substantially transverse or orthogonal to a general direction of flow of the first fluid makes it possible to avoid the creation of one or more zones at the level of which the flow, and therefore the heat exchange, is low or even zero. This arrangement of said intermediate ports 69b, 75, 73 allows a better use of the space by maximizing the heat exchange zones.
    [0016] Said intermediate orifices 69b, 73, 75 advantageously have an oblong and elongated shape in the direction of longitudinal extension of the plate 3. Each of said intermediate orifices 69b, 73, 75 advantageously extends between two opposite longitudinal ends of said orifice. one of the other along said main direction of longitudinal extension of the plate. Said intermediate orifices 69b, 73, 75 have a width, measured in a direction transverse to said main direction of longitudinal extension, which decreases over almost the entire length of the orifice between the two longitudinal ends. The portion of the orifice having the largest width is located upstream of the portion of the orifice having the smallest width in the direction of flow of the second fluid. In other words, said intermediate orifices 69b, 75, 73 have a pear shape whose widest part is located upstream of the narrowest part in the direction of flow of said second fluid. This shape of said intermediate orifices 69b, 75, 73 makes it possible to reduce the pressure losses generated by the circulation of the second fluid on the plates 3 at the level of said intermediate orifices 69b, 75, 73.
    [0017] Said plates 3 comprise several types of plates 3 among which are primary plates 3a, illustrated in FIGS. 4, 6 and 9, and secondary plates 3b, illustrated in FIGS. 5, 7 and 8. Said primary plates 3a are designed so that the first fluid circulates on their front and the second fluid flows on their back. Said secondary plates 3b are designed so that the second fluid can circulate on their front and the first fluid can flow on their back. It is the alternation of one of the primary plates 3a with one of the secondary plates 3b which allows the stack of plates to create said circuits for the first fluid and for the second fluid. Said plates 3 are used in pairs, each pair of plates 3 comprising one of the primary plates 3a and one of the secondary plates 3b.
    [0018] In particular, as regards the circuit for the first fluid, each passage 7 for the first fluid is defined by a circulation space between the front of one of the primary plates 3a and the back of one of the secondary plates 3b, said two primary and secondary plates 3a and 3b being adjacent to each other. Regarding the second fluid, each passage 9 for the second fluid is defined by a circulation space between the front of one of the secondary plates 3b and the back of one of the primary plates 3a, said two primary plates 3a and secondary 3b being adjacent to each other. In the case of a secondary plate 3b, each of the first 73, second 69b and third 75 intermediate ports, respectively, is located in a swelling forming a convex region 73 ', 69b' and 75 ', each of said convex regions 73', 69b 'and 75' being arranged within a planar region 67 forming a bottom of the plate. It will furthermore be noted that each secondary plate 3b is designed such that said second fluid can flow, on the front of said plate, at the level of the plane region 67 between said curved regions 73 ', 69b' and 75 'surrounding each orifice 73, 69b, 65 and directly from the first portion 130 to the second portion 150 of said secondary plate 3b. In other words, said secondary plate 3b is designed so that said second fluid can flow, on the front thereof, from the first portion 130 to the second portion 150 of said plate bypassing each of the orifices 73, 69b, 75 and thus without circulating inside the manifolds 51b, 55 and 53. Said three curved regions 69b ', 75' and 73 'of the secondary plate are intended respectively to correspond with plane regions 69b ", 75" and 73 " of an adjacent primary plate 3a, that is, said curved regions 69b ', 75' and 73 'and said planar regions 69b ", 75" and 73 "are intended, once the plates 3 stacked on top of one another, to be in touch. In each of the primary plates 3a, said intermediate ports 69b, 75 and 73 are each disposed within said planar regions 69b ", 75" and 73 ", respectively.
    [0019] Advantageously, said planar regions 69b ", 75" and 73 "each have a shape substantially identical to each intermediate orifice and dimensions slightly greater than these, in other words, on the primary plates 3a, each of said planar regions 69b", 75 "and 73" surround the corresponding intermediate orifice 69b, 75 and 73. Said planar regions 69b ", 75" and 73 "of the primary plates 3a are substantially identical in shape and size to the curved regions 69b ', 75' and 73 'of the secondary plates 30b and 3b so as to facilitate the joining between the regions. planes 69b ", 75" and 73 "and curved regions 69b ', 75' and 73 '. In particular, the front of said curved regions 69b ', 75' and 73 'of each secondary plate 3b is configured to be in contact with the back of the region of the planar regions 69b ", 75" and 73 "of a primary plate 3a of primary plates 3a there are still primary plates of a first type 3a 'illustrated in FIG. 4 and primary plates of a second type 3a' illustrated in FIG. Secondary plates 3b with one of the primary plates of the first type 3a 'makes it possible to form a pair of first type. The combination of one of the secondary plates 3b with one of the primary plates of the second type 3a "makes it possible to form a pair of second type The pairs of plates of the first type are configured to allow the circulation of the first fluid in the passes 25a and 25b, or even 25c, the pairs of plates of the second type are configured to allow the first fluid to flow between the first and third intermediate manifolds 53, 55, at the level of the passage 25c, in other words, the passes 25a and 25c. 25b comprise pairs of plates 3 of the first type while the pass 25c comprises at least one pair of plates 3 of the second type and, possibly, pairs of plates of the first type, it is noted that the secondary plates 3b, they are advantageously identical in all the passes and therefore regardless of the type of pairs of plates 3, except to be provided with a partition 57, as developed later.
    [0020] In both types of pairs, the primary plate 3a is provided on its front with a stamp formed of a convex region 65 intended to be in contact with the back of a secondary plate 3b, at said level region 67 of it. It will be noted that said curved region 65 of the primary plate 3a is arranged between the first 130 and second 150 part of said plate 3a, at the level of the intermediate orifices 69b, 75, 73. Likewise, the plane region 67 of the secondary plates 3b is arranged between the portion 130 and the portion 150. In particular, said convex region 65 extends substantially transversely from one of the lateral edges 34 to the other of the lateral edges 34 of the primary plate 3a, so that the direct passage of said first fluid is made impossible from the first zone 13 to the second zone 15. In the pairs of the first type, said curved region 65 of the primary plate of the first type 3a 'and said flat region 67 of the secondary plate are designed to, by their junction, prevent the flow of the first fluid between firstly the first portion 13 and secondly the second intermediate orifice 69b and the first intermediate orifice 75, while allowing the circulation of the first fluid between the first zone 13 and the orifice 73 as well as between the second intermediate orifice 69b and the second zone 13. In other words, said curved region 65 of the primary plate of the first type 3a 'and said The flat region 67 of the secondary plate 3b is designed to prevent the flow of the first fluid between the first zone 13 of the bundle 1 and the first and second intermediate manifolds 55, 51b. More precisely, in the plates 3 of the pairs of the first type, said convex region 65 first bypasses the plane region 69h "and said second intermediate orifice 69b so as to isolate said second intermediate orifice 69b from the first portion 13. The orifice 75 and the flat region 75 "are then completely surrounded by the domed region 65 so that said orifice 75 is designed to be insulated from both the first portion 13 and the second first portion 15. Finally, the domed region 65 bypasses the plane region 73 "and the third intermediate orifice 73 so as to separate said third intermediate orifice 73 from the second portion 15 of the primary plate of the first type 3a '.
    [0021] The pairs of the second type, that is to say those arranged in the last pass 25c, differ from the pairs of the first type in that, here, said curved region 65 of the primary plate of the second type 3a "is this once designed to, by its junction with the plane region 67 of the secondary plate 3b, allow the direct flow of the first fluid between the first zone 13 and the first intermediate manifold 55. In other words, the primary plates of the second type 3a "are designed to allow a passage between the first zone 13 and the bottle 11. More specifically, in the plates of the pairs of the second type, said convex region 65 of the primary plate beta 3a "first bypasses the plane region 69h" and said second intermediate orifice 69b so as to isolate said second intermediate orifice 69b from the first portion 13. The planar region 75 "and the first intermediate orifice 75 are then separated from the second part 15 of the primary plate of the second type 3a "by the convex region 65. Finally, the plane region 73" and the third intermediate orifice 73 are also separated from the second part 15 of the primary plate of the second type 3a "by said region In Figure 7, the secondary plate 3b differs from that illustrated in Figure 5 in that the orifice 73 15 is here provided with one of said partition 57. Advantageously, in a heat exchanger, the beam 1 comprises at least one such plate 3. Note that the partition wall 57 are for example derived from material with the convex region 73 '. The circulation of the second fluid does not depend on the type of plate pair 3. The same type of passage is defined guiding the second fluid from the inlet manifold of the second fluid to the outlet manifold of the second fluid. In general, it will be noted that the circulation of each fluid within a pair of plates is constrained by the junction of the front of a domed region of one of the plates 3 with the back of a flat region of a plate 3 adjacent, said fluid being forced to bypass said junction. In other words, the contact area between one of the curved regions and the planar surface is inaccessible to said first and second fluids.
    [0022] It will also be appreciated that said domed region 65 is designed to prevent a direct flow of the first fluid from one manifold to another. In other words, said curved zone 65 is furthermore designed so as to prevent the circulation of the first fluid, between two plates 3 of the same pair, from an intermediate orifice to another intermediate orifice, except at the level of the pairs of the second type. Said plates 3 may also be provided with corrugations 77 on the bottom of the plate arranged so as to create disturbances in the fluids and / or points of contact between the plates 3. Said corrugations thus make it possible to improve the exchange of heat between the first fluid and the second fluid.
    [0023] Alternatively, as illustrated in FIG. 2, the first zone 13 of the heat exchanger defines a single-pass configuration. This configuration is here obtained using only secondary plates 3b, all provided with partition walls 57, as illustrated in FIG. 7, and primary plates of the second type 3a "as illustrated in FIG.
    [0024] Alternatively, as illustrated in FIGS. 10 and 11, plates 3 without a third intermediate orifice may be used. Advantageously, the other characteristics of the one-pass heat exchanger are similar to those of the three-pass heat exchanger.
    权利要求:
    Claims (10)
    [0001]
    REVENDICATIONS1. heat exchanger comprising a plurality of stacked plates (3) intended to allow a heat exchange between a first fluid and a second fluid flowing in contact with said plates (3), said exchanger comprising a bottle (11) for the first fluid, said plates (3) being provided with intermediate orifices (69b, 75) permitting a circulation of the first fluid between said plates (3) and said bottle (11), said intermediate orifices (69b, 75) being arranged along a direction substantially transverse to a main direction of longitudinal extension of each plate (3).
    [0002]
    2. [heat changer according to the preceding claim, wherein said plates (3) are configured to define each two parts (130, 150) including a first portion (130) to allow a heat exchange between the first fluid and the second fluid before passage of the first fluid in the bottle (11) and a second portion (150) to allow heat exchange between the first fluid and the second fluid after passage of the first fluid in the bottle (11), said intermediate ports (69b , 75) being arranged between said first (130) and second (150) parts.
    [0003]
    The heat exchanger according to the preceding claim, wherein said first portions (130) of the plates (3) define a condensing zone (13) and said second portions (150) define a subcooling zone (15).
    [0004]
    4. [heat exchanger according to the preceding claim, wherein a first of said intermediate ports (69b, 75) allows a flow of the first fluid from the condensation zone (13) to the bottle (11), a second of said intermediate ports ( 69b, 75) allowing a flow of the first fluid from the bottle (11) to the subcooling zone (15). 3035488 19
    [0005]
    A heat exchanger according to any one of the preceding claims, wherein the plates (3) further comprise an additional orifice (73), said through-flow orifice, aligned with said first and second intermediate ports (69b, 75).
    [0006]
    6. [heat exchanger according to the preceding claim, wherein the orifice (73) for passing through at least one of the plates (3), said secondary plate, is obstructed to allow the circulation of said first fluid. in several passes in the zone 10 of condensation (13).
    [0007]
    A heat exchanger according to any one of the preceding claims, wherein the bottle (11) extends in said main direction of the plates. 15
    [0008]
    A heat exchanger according to any one of the preceding claims, wherein, said heat exchanger being provided with inlet manifolds (19i) and outlet manifolds (19o), said bottle (11) and said manifolds ( 19i, 19o) are located on the same side (17) of the heat exchanger, said upper side. 20
    [0009]
    9. [heat exchanger according to any one of the preceding claims, wherein said intermediate ports (69b, 75) have an oblong shape and / or elongated in a direction of flow of said second fluid (3).
    [0010]
    10. [The heat exchanger according to the preceding claim, in each of said intermediate orifices (69b, 75, 73) has a width, measured in a direction transverse to said main direction of longitudinal extension, which decreases over almost the entire length of the orifice in a direction of flow of said second fluid.
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    FR3030710A1|2016-06-24|COLLECTOR BOX FOR HEAT EXCHANGER AND HEAT EXCHANGER EQUIPPED WITH SAID COLLECTOR BOX
    EP3449197B1|2019-12-11|Heat exchanger made from plastic material and vehicle comprising said heat exchanger
    EP3274644B1|2019-03-06|Collecting box for a heat exchanger of a motor vehicle air-conditioning circuit, and heat exchanger comprising such a collecting box
    FR3024771A1|2016-02-12|HEAT EXCHANGER BEAM AND HEAT EXCHANGER COMPRISING SAID BEAM
    FR3001795A1|2014-08-08|Heat exchanger arrangement for air-conditioning circuit of air-conditioning device in modern vehicle, has channel distributer and collector extending longitudinally in parallelepipedic block and are in connection with continuous spaces
    FR3066261A1|2018-11-16|HEAT EXCHANGER OPTIMIZED WITH THREE ROWS OF TUBES
    FR2973491A1|2012-10-05|Plate for heat exchanger used as charge air cooler in car, has passages arranged parallel to each other in extension direction, where width of plate is orthogonal to extension direction, and number of passages is chosen based on plate width
    FR3045804A1|2017-06-23|THERMAL EXCHANGER, IN PARTICULAR FOR MOTOR VEHICLE
    WO2017109348A1|2017-06-29|Heat exchanger, in particular for a motor vehicle
    WO2018134444A1|2018-07-26|Refrigerant circulation circuit for a two-layer evaporator
    EP3394555A1|2018-10-31|Heat exchanger, notably for motor vehicle
    FR3066812A1|2018-11-30|AIL FOR HEAT EXCHANGER INCLUDING TWO SCRATCHES
    FR3067797A1|2018-12-21|EVAPORATOR HAVING TWO TABS, ESPECIALLY FOR A MOTOR VEHICLE AIR CONDITIONING CIRCUIT, COMPRISING "U" TUBES AND CORRESPONDING AIR CONDITIONING CIRCUIT
    同族专利:
    公开号 | 公开日
    EP3289302B1|2019-11-13|
    KR20170140338A|2017-12-20|
    EP3289302A1|2018-03-07|
    WO2016173935A1|2016-11-03|
    CN107949761A|2018-04-20|
    FR3035488B1|2018-05-18|
    JP2018514741A|2018-06-07|
    JP6554182B2|2019-07-31|
    US20180120033A1|2018-05-03|
    KR102038213B1|2019-10-29|
    引用文献:
    公开号 | 申请日 | 公开日 | 申请人 | 专利标题
    FR3000183A1|2012-12-21|2014-06-27|Valeo Systemes Thermiques|CONDENSER WITH FRIGORIGENE FLUID RESERVE FOR AIR CONDITIONING CIRCUIT|
    FR3001796A1|2013-02-07|2014-08-08|Delphi Automotive Systems Lux|Condenser and sub-cooler arrangement for air-conditioning circuit of vehicle, has drain for connecting receiver-dehumidifier to inlet of channel, so that fluid circulates successively in condenser, receiver-dehumidifier and sub-cooler|
    DE102013214695A1|2013-07-26|2015-01-29|Behr Gmbh & Co. Kg|capacitor|FR3086379A1|2018-09-25|2020-03-27|Valeo Systemes Thermiques|OPTIMIZED OPENING HEAT EXCHANGER PLATE|US2939686A|1955-02-04|1960-06-07|Cherry Burrell Corp|Double port heat exchanger plate|
    US4182411A|1975-12-19|1980-01-08|Hisaka Works Ltd.|Plate type condenser|
    JPH0875317A|1994-09-07|1996-03-19|Calsonic Corp|Condenser with liquid receiver|
    SE516416C2|2000-05-19|2002-01-15|Alfa Laval Ab|Plate package, heat transfer plate, plate heat exchanger and use of heat transfer plate|
    DE10049890B4|2000-10-10|2007-02-22|Behr Gmbh & Co. Kg|Stacked-plate heat exchanger|
    FR2870588B1|2004-05-18|2007-01-05|Valeo Thermique Moteur Sas|HEAT EXCHANGER FOR ENGINE OIL OF A VEHICLE|
    WO2009013801A1|2007-07-23|2009-01-29|Tokyo Roki Co. Ltd.|Plate laminate type heat exchanger|
    FR2943774B1|2009-03-24|2013-12-20|Valeo Systemes Thermiques|CONDENSER HAVING TWO HEAT EXCHANGE BLOCKS FOR AIR CONDITIONING CIRCUIT|
    JP5960955B2|2010-12-03|2016-08-02|現代自動車株式会社Ｈｙｕｎｄａｉ Ｍｏｔｏｒ Ｃｏｍｐａｎｙ|Vehicle capacitors|
    JP5085723B2|2010-12-13|2012-11-28|株式会社日阪製作所|Plate heat exchanger|
    KR101316859B1|2011-12-08|2013-10-10|현대자동차주식회사|Condenser for vehicle|
    FR2986315B1|2012-01-30|2014-01-10|Valeo Systemes Thermiques|HEAT EXCHANGER|
    PL2927631T3|2014-03-31|2019-04-30|Valeo Autosystemy Sp Z O O|Heat exchanger, especially a condenser|
    FR3059400A1|2016-11-25|2018-06-01|Valeo Systemes Thermiques|HEAT EXCHANGER BETWEEN A REFRIGERANT FLUID AND A COOLANT LIQUID|JP6497262B2|2014-10-30|2019-04-10|株式会社デンソー|Laminate heat exchanger|
    US10591220B2|2017-08-31|2020-03-17|Dana Canada Corporation|Multi-fluid heat exchanger|
    法律状态:
    2016-04-28| PLFP| Fee payment|Year of fee payment: 2 |
    2016-10-28| PLSC| Search report ready|Effective date: 20161028 |
    2017-04-28| PLFP| Fee payment|Year of fee payment: 3 |
    2018-04-26| PLFP| Fee payment|Year of fee payment: 4 |
    2019-04-29| PLFP| Fee payment|Year of fee payment: 5 |
    2020-04-30| PLFP| Fee payment|Year of fee payment: 6 |
    2021-04-29| PLFP| Fee payment|Year of fee payment: 7 |
    优先权:
    申请号 | 申请日 | 专利标题
    FR1553779|2015-04-27|
    FR1553779A|FR3035488B1|2015-04-27|2015-04-27|HEAT EXCHANGER WITH STACKED PLATES|FR1553779A| FR3035488B1|2015-04-27|2015-04-27|HEAT EXCHANGER WITH STACKED PLATES|
    JP2017556199A| JP6554182B2|2015-04-27|2016-04-22|Heat exchanger having a plurality of stacked plates|
    PCT/EP2016/058974| WO2016173935A1|2015-04-27|2016-04-22|Heat exchanger with stacked plates|
    US15/569,325| US20180120033A1|2015-04-27|2016-04-22|Heat exchanger with stacked plates|
    EP16717658.5A| EP3289302B1|2015-04-27|2016-04-22|Heat exchanger with stacked plates|
    KR1020177034075A| KR102038213B1|2015-04-27|2016-04-22|Heat exchanger with laminated plate|
    CN201680031297.5A| CN107949761A|2015-04-27|2016-04-22|Heat exchanger with stacking plate|
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