EP1809958A2 - Parallel flow evaporator with variable channel insertion depth - Google Patents

Parallel flow evaporator with variable channel insertion depth

Info

Publication number
EP1809958A2
EP1809958A2 EP05817473A EP05817473A EP1809958A2 EP 1809958 A2 EP1809958 A2 EP 1809958A2 EP 05817473 A EP05817473 A EP 05817473A EP 05817473 A EP05817473 A EP 05817473A EP 1809958 A2 EP1809958 A2 EP 1809958A2
Authority
EP
European Patent Office
Prior art keywords
inlet manifold
channels
heat exchanger
parallel
manifold
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP05817473A
Other languages
German (de)
French (fr)
Other versions
EP1809958B1 (en
EP1809958A4 (en
Inventor
Michael F. Taras
Allen C. Kirkwood
Robert A. Chopko
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Carrier Corp
Original Assignee
Carrier Corp
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Carrier Corp filed Critical Carrier Corp
Publication of EP1809958A2 publication Critical patent/EP1809958A2/en
Publication of EP1809958A4 publication Critical patent/EP1809958A4/en
Application granted granted Critical
Publication of EP1809958B1 publication Critical patent/EP1809958B1/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B39/00—Evaporators; Condensers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
    • F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
    • F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
    • F28D1/053—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being straight
    • F28D1/0535—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being straight the conduits having a non-circular cross-section
    • F28D1/05366—Assemblies of conduits connected to common headers, e.g. core type radiators
    • F28D1/05383—Assemblies of conduits connected to common headers, e.g. core type radiators with multiple rows of conduits or with multi-channel conduits
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02—Header boxes; End plates
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02—Header boxes; End plates
    • F28F9/026—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits
    • F28F9/0282—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits by varying the geometry of conduit ends, e.g. by using inserts or attachments for modifying the pattern of flow at the conduit inlet or outlet
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2500/00—Problems to be solved
    • F25B2500/01—Geometry problems, e.g. for reducing size
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
    • F28D2021/0019—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for
    • F28D2021/0068—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for refrigerant cycles
    • F28D2021/0071—Evaporators

Definitions

  • This invention relates generally to air conditioning and refrigeration systems and, more particularly, to parallel flow evaporators thereof.
  • a definition of a so-called parallel flow heat exchanger is widely used in the air conditioning and refrigeration industry now and designates a heat exchanger with a plurality of parallel passages, among which refrigerant is distributed and flown in the orientation generally substantially perpendicular to the refrigerant flow direction in the inlet and outlet manifolds. This definition is well adapted within the technical community and will be used throughout the text.
  • Refrigerant maldistribution in refrigerant system evaporators is a well-known phenomenon. It causes significant evaporator and overall system performance degradation over a wide range of operating conditions.
  • Maldistribution of refrigerant may occur due to differences in flow impedances within evaporator channels, non-uniform airflow distribution over external heat transfer surfaces improper heat exchanger orientation or poor manifold and distribution system design. Maldistribution is particularly pronounced in parallel flow evaporators due to their specific design with respect to refrigerant routing to each refrigerant circuit. Attempts to eliminate or reduce the effects of this phenomenon on the performance of parallel flow evaporators have been made with little or no success. The primary reasons for such failures have generally been related to complexity and inefficiency of the proposed technique or prohibitively high cost of the solution.
  • the inlet and outlet manifolds or headers usually have a conventional cylindrical shape.
  • the vapor phase is usually separated from the liquid phase. Since both phases flow independently, refrigerant maldistribution tends to occur.
  • the liquid phase (droplets of liquid) is carried by the momentum of the flow further away from the manifold entrance to the remote portion of the header.
  • the channels closest to the manifold entrance receive predominantly the vapor phase and the channels remote from the manifold entrance receive mostly the liquid phase.
  • the velocity of the two-phase flow entering the manifold is low, there is not enough momentum to carry the liquid phase along the header.
  • the liquid phase enters the channels closest to the inlet and the vapor phase proceeds to the most remote ones.
  • the liquid and vapor phases in the inlet manifold can be separated by the gravity forces, causing similar maldistribution consequences. In either case, maldistribution phenomenon quickly surfaces and manifests itself in evaporator and overall system performance degradation.
  • the insertion depth of the individual parallel channels into the inlet manifold is varied so as to obtain a more uniform refrigerant distribution to the individual channels by way of the differential pressure drop that is created by the variable insertion depth. In this way, a two-phase refrigerant mixture is more uniformly distributed among the channels.
  • the insertion depth of the individual channels is progressively smaller toward the downstream end of the inlet manifold such that the hydraulic resistance to flow is progressively lower toward the downstream channels.
  • variable insertion depth of the individual channels is accommodated by appropriately enlarging the diameter of the inlet manifold.
  • the enlargement can be uniform in a cross-section perpendicular to the refrigerant flow to result in a cylindrical inlet manifold or it can be variable such that the portions immediately surrounding the individual channels are larger and the portions therebetween are smaller.
  • the insertion depth of the individual channels into the outlet manifold is also varied to compensate for variable flow impedance in the outlet manifold as well.
  • FIG. 1 is a schematic illustration of a parallel flow heat exchanger in accordance with the prior art.
  • FIGS. 2 and 3 are schematic illustrations of one embodiment of the present invention.
  • FIGS. 4A, 4B and 4C are schematic illustrations of other embodiments of the present invention.
  • FIG. 5 is a schematic illustration of yet another embodiment of the present invention.
  • a parallel flow heat exchanger is shown to include an inlet header or manifold 11, an outlet header or manifold 12 and a plurality of parallel disposed channels 13 fluidly interconnecting the inlet manifold 11 to the outlet manifold 12.
  • the inlet and outlet manifolds 11 and 12 are cylindrical in shape, and the channels 13 are usually tubes (or extrusions) of flattened or round shape.
  • Channels 13 normally have a plurality of internal and external heat transfer enhancement elements, such as fins. For instance, external fins, disposed therebetween for the enhancement of the heat exchange process and structural rigidity, are typically furnace-brazed.
  • Channels 13 may have internal heat transfer enhancements and structural elements as well.
  • Fig. 2 the present invention is illustrated in accordance with one embodiment.
  • the penetration thereinto is variable, depending on the position along the longitudinal axis A.
  • the channel 21 closest to the inlet 14 penetrates the furthest into the internal cavity 16 and those following (i.e. channels 22 and 23) are so placed and installed with respect to the inlet manifold 11 so as to have progressively smaller insertion depths as shown.
  • the two-phase refrigerant enters the internal cavity 16 by way of the inlet 14 and, because of the limited distance between the penetrating end 24 of tube 21 and the opposing wall 28 of the inlet manifold 11, there would be increased hydraulic resistance and therefore restricted flow into the channel 21.
  • the next channel 22, with its reduced insertion depth, provides a greater distance between the end 26 and the wall 28.
  • the next downstream channel 23 has its end 27 inserted an even smaller distance into the cavity, and any subsequent channels are progressively decreased in their insertion depth. Therefore, the problem of the more upstream tubes receiving a greater portion of the refrigerant is overcome by selectively varying the impedance to the flow at the entrance into each of the channels. Additionally, increased velocity of the refrigerant flow in the inlet manifold 16 may promote more homogeneous conditions through mixing and jetting effects.
  • each section having equal insertion depth and with the insertion depth varying from section to section and decreasing in the downstream direction along the inlet manifold.
  • each individual channel shown in Fig. 2 would represent a section of such channels for a sufficiently large heat exchanger.
  • the Fig. 2 illustration is presented in exaggerated form for demonstrative purposes. Therefore, in order to understand the magnitudes of the insertion depth for a typical design, exemplary measurements will be provided.
  • the insertion depth Li of the first tube 21 would preferably be in the range of 7/8".
  • the next channel 22 would have an insertion depth Of(Li-L 2 ) or (7/8"- 1/16"), and each succeeding tube would have a diminishing insertion depth by L 2 1/16".
  • the insertion depth Li of the individual channels depends on many parameters, including the heat exchanger size, channel size and number, typical operating range, refrigerant and oil type circulating through the system, etc. [0025] As is seen in Fig.
  • the relatively wide channels 21, 22 and 23, which occupy a large part of the cross-section area of the inlet manifold 11, may each introduce undesired impedance to the refrigerant flow along the longitudinal axis of the inlet manifold 11. This may be accommodated by an increase in the diameter D of the inlet manifold 11.
  • FIG. 4A Rather than increasing the diameter D of the inlet manifold 11 along its entire longitudinal axis, an alternative design is shown in Fig. 4A wherein the cross-section area of a header 31 is enlarged only in the immediate vicinity of the insertion points of the channels 21, 22 and 23 into the header 31. In this way, the restriction to the refrigerant flow around the ends of the channels is avoided or limited so as to promote favorable uniform conditions to the refrigerant flow into the channels, as desired.
  • the form and shape of the enlargements may vary, the wavy shape tends to provide a smoother, less disturbed motion of the refrigerant passing along the inlet header and would be preferred.
  • an inlet manifold can be made of an oval or rectangular shape as shown by 37 and 38 respectively, without appreciably increasing its overall cross-section area. This will prevent refrigerant flow velocity reduction and potential undesired phase separation.
  • a similar technique can be applied to the outlet manifold 41, with the downstream channels having higher insertion depths. Although the outlet manifold (typically having a single phase refrigerant vapor) has a less pronounced influence on the refrigerant distribution among the channels, such balancing of the flow impedances will further assist in the maldistribution problem resolution.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Geometry (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
  • Details Of Heat-Exchange And Heat-Transfer (AREA)

Abstract

In a parallel flow heat exchanger having an inlet manifold connected to a plurality of parallel channels, the degree of insertion depth of the parallel channels into the inlet manifold is variable so as to adjust the impedance to the refrigerant flow into the individual channels. The degree of insertion depth is progressively reduced toward a downstream end of the manifold for the individual channels or for the channel sections. The diameter of the inlet manifold is locally increased or its cross-section area altered in order to accommodate the flow of refrigerant around the tube insertions. Similar technique is applied to the outlet manifold as well to further balance hydraulic resistances.

Description

Parallel Flow Evaporator with Variable Channel Insertion Depth
Background of the Invention
[0001] This invention relates generally to air conditioning and refrigeration systems and, more particularly, to parallel flow evaporators thereof. [0002] A definition of a so-called parallel flow heat exchanger is widely used in the air conditioning and refrigeration industry now and designates a heat exchanger with a plurality of parallel passages, among which refrigerant is distributed and flown in the orientation generally substantially perpendicular to the refrigerant flow direction in the inlet and outlet manifolds. This definition is well adapted within the technical community and will be used throughout the text. [0003] Refrigerant maldistribution in refrigerant system evaporators is a well-known phenomenon. It causes significant evaporator and overall system performance degradation over a wide range of operating conditions. Maldistribution of refrigerant may occur due to differences in flow impedances within evaporator channels, non-uniform airflow distribution over external heat transfer surfaces improper heat exchanger orientation or poor manifold and distribution system design. Maldistribution is particularly pronounced in parallel flow evaporators due to their specific design with respect to refrigerant routing to each refrigerant circuit. Attempts to eliminate or reduce the effects of this phenomenon on the performance of parallel flow evaporators have been made with little or no success. The primary reasons for such failures have generally been related to complexity and inefficiency of the proposed technique or prohibitively high cost of the solution. [0004] In recent years, parallel flow heat exchangers, and brazed aluminum heat exchangers in particular, have received much attention and interest, not just in the automotive field but also in the heating, ventilation, air conditioning and refrigeration (HVAC&R) industry. The primary reasons for the employment of the parallel flow technology are related to its superior performance, high degree of compactness and enhanced resistance to corrosion. Parallel flow heat exchangers are now utilized in both condenser and evaporator applications for multiple products and system designs and configurations. The evaporator applications, although promising greater benefits and rewards, are more challenging and problematic. Refrigerant maldistribution is one of the primary concerns and obstacles for the implementation of this technology in the evaporator applications. [0005] As known, refrigerant maldistribution in parallel flow heat exchangers occurs because of unequal pressure drop inside the channels and in the inlet and outlet manifolds, as well as poor manifold and distribution system design. In the manifolds, the difference in length of refrigerant paths, phase separation, gravity and turbulence are the primary factors responsible for maldistribution. Inside the heat exchanger channels, variations in the heat transfer rate, airflow distribution, manufacturing tolerances, and gravity are the dominant factors. Furthermore, the recent trend of the heat exchanger performance enhancement promoted miniaturization of its channels (so-called minichannels and microchannels), which in turn negatively impacted refrigerant distribution. Since it is extremely difficult to control all these factors, many of the previous attempts to manage refrigerant distribution, especially in parallel flow evaporators, have failed. [0006] In the refrigerant systems utilizing parallel flow heat exchangers, the inlet and outlet manifolds or headers (these terms will be used interchangeably throughout the text) usually have a conventional cylindrical shape. When the two- phase flow enters the header, the vapor phase is usually separated from the liquid phase. Since both phases flow independently, refrigerant maldistribution tends to occur.
[0007] If the two-phase flow enters the inlet manifold at a relatively high velocity, the liquid phase (droplets of liquid) is carried by the momentum of the flow further away from the manifold entrance to the remote portion of the header. Hence, the channels closest to the manifold entrance receive predominantly the vapor phase and the channels remote from the manifold entrance receive mostly the liquid phase. If, on the other hand, the velocity of the two-phase flow entering the manifold is low, there is not enough momentum to carry the liquid phase along the header. As a result, the liquid phase enters the channels closest to the inlet and the vapor phase proceeds to the most remote ones. Also, the liquid and vapor phases in the inlet manifold can be separated by the gravity forces, causing similar maldistribution consequences. In either case, maldistribution phenomenon quickly surfaces and manifests itself in evaporator and overall system performance degradation. Summary of the Invention
[0008] Briefly, in accordance with one aspect of the invention, the insertion depth of the individual parallel channels into the inlet manifold is varied so as to obtain a more uniform refrigerant distribution to the individual channels by way of the differential pressure drop that is created by the variable insertion depth. In this way, a two-phase refrigerant mixture is more uniformly distributed among the channels.
[0009] In accordance with another aspect of the invention, the insertion depth of the individual channels is progressively smaller toward the downstream end of the inlet manifold such that the hydraulic resistance to flow is progressively lower toward the downstream channels.
[0010] In accordance with another aspect of the invention, the variable insertion depth of the individual channels is accommodated by appropriately enlarging the diameter of the inlet manifold. The enlargement can be uniform in a cross-section perpendicular to the refrigerant flow to result in a cylindrical inlet manifold or it can be variable such that the portions immediately surrounding the individual channels are larger and the portions therebetween are smaller.
[0011] In accordance with yet another aspect of the invention, the insertion depth of the individual channels into the outlet manifold is also varied to compensate for variable flow impedance in the outlet manifold as well.
[0012] In the drawings as hereinafter described, preferred and alternate embodiments are depicted; however, various other modifications and alternate constructions can be made thereto without departing from the true spirit and scope of the invention.
Brief Description of the Drawings
[0013] FIG. 1 is a schematic illustration of a parallel flow heat exchanger in accordance with the prior art.
[0014] FIGS. 2 and 3 are schematic illustrations of one embodiment of the present invention.
[0015] FIGS. 4A, 4B and 4C are schematic illustrations of other embodiments of the present invention. [0016] FIG. 5 is a schematic illustration of yet another embodiment of the present invention.
Description of the Preferred Embodiment
[0017] Referring now to Fig. 1, a parallel flow heat exchanger is shown to include an inlet header or manifold 11, an outlet header or manifold 12 and a plurality of parallel disposed channels 13 fluidly interconnecting the inlet manifold 11 to the outlet manifold 12. Generally, the inlet and outlet manifolds 11 and 12 are cylindrical in shape, and the channels 13 are usually tubes (or extrusions) of flattened or round shape. Channels 13 normally have a plurality of internal and external heat transfer enhancement elements, such as fins. For instance, external fins, disposed therebetween for the enhancement of the heat exchange process and structural rigidity, are typically furnace-brazed. Channels 13 may have internal heat transfer enhancements and structural elements as well.
[0018] The usual manner of attaching the parallel channels 13 to the inlet manifold 11 and the outlet manifold 12 is to insert the channels 13 so that they extend into the internal cavities of the inlet and outlet manifolds 11 and 12 as shown by the dotted lines. The usual practice is to have equal insertion depth for each of the channels 13. They are then fixed in position by way of brazing or the like. [0019] In operation, two-phase refrigerant flows into the inlet opening 14 and into the internal cavity 16 of the inlet header 11. From the internal cavity 16, the refrigerant, in the form of a liquid, a vapor or a mixture of liquid and vapor (the most typical scenario) enters the tube openings 17 to pass through the channels 13 to the internal cavity 18 of the outlet header 12. From there, the refrigerant, which is now usually in the form of a vapor, passes out the outlet opening 19 and then to the compressor (not shown).
[0020] As discussed hereinabove, it is desirable that the two-phase refrigerant passing from the inlet header 11 to the individual channels 13 do so in a uniform manner (or in other words, with equal vapor quality) such that the full heat exchange benefit of the individual channels can be obtained and flooding conditions are not created and observed at the compressor suction (this may damage the compressor). However, because of various phenomena as discussed hereinabove, a non-uniform flow of refrigerant to the individual channels 13 (so-called maldistribution) occurs. In order to address this problem, the applicants have introduced design features that will create different pressure drop for flow of refrigerant from the inlet manifold to the individual channels to thereby bring about a more uniform flow of refrigerant into the channels 13. Additionally, increased velocity of the refrigerant flow in the inlet manifold promotes more homogeneous conditions through mixing and jetting effects.
[0021] Referring now to Fig. 2, the present invention is illustrated in accordance with one embodiment. Here, instead of the channels 13 penetrating equally into the internal cavity 16 of the inlet manifold 11, the penetration thereinto is variable, depending on the position along the longitudinal axis A. As shown, the channel 21 closest to the inlet 14 penetrates the furthest into the internal cavity 16 and those following (i.e. channels 22 and 23) are so placed and installed with respect to the inlet manifold 11 so as to have progressively smaller insertion depths as shown.
[0022] In operation, the two-phase refrigerant enters the internal cavity 16 by way of the inlet 14 and, because of the limited distance between the penetrating end 24 of tube 21 and the opposing wall 28 of the inlet manifold 11, there would be increased hydraulic resistance and therefore restricted flow into the channel 21. The next channel 22, with its reduced insertion depth, provides a greater distance between the end 26 and the wall 28. The next downstream channel 23 has its end 27 inserted an even smaller distance into the cavity, and any subsequent channels are progressively decreased in their insertion depth. Therefore, the problem of the more upstream tubes receiving a greater portion of the refrigerant is overcome by selectively varying the impedance to the flow at the entrance into each of the channels. Additionally, increased velocity of the refrigerant flow in the inlet manifold 16 may promote more homogeneous conditions through mixing and jetting effects.
[0023] It has to be noted that if it becomes difficult to control the insertion depth of the individual channels during the manufacturing processes due to a sufficiently large number of channels, then the insertion depth can be controlled in sections with each section having equal insertion depth and with the insertion depth varying from section to section and decreasing in the downstream direction along the inlet manifold. In such case, each individual channel shown in Fig. 2 would represent a section of such channels for a sufficiently large heat exchanger. [0024] The Fig. 2 illustration is presented in exaggerated form for demonstrative purposes. Therefore, in order to understand the magnitudes of the insertion depth for a typical design, exemplary measurements will be provided. Considering an inlet manifold 11 having a typical diameter D of 1", the insertion depth Li of the first tube 21 would preferably be in the range of 7/8". The next channel 22 would have an insertion depth Of(Li-L2) or (7/8"- 1/16"), and each succeeding tube would have a diminishing insertion depth by L2 1/16". It has to be understood the insertion depth Li of the individual channels depends on many parameters, including the heat exchanger size, channel size and number, typical operating range, refrigerant and oil type circulating through the system, etc. [0025] As is seen in Fig. 3, because of increased insertion depths as compared with the prior art, the relatively wide channels 21, 22 and 23, which occupy a large part of the cross-section area of the inlet manifold 11, may each introduce undesired impedance to the refrigerant flow along the longitudinal axis of the inlet manifold 11. This may be accommodated by an increase in the diameter D of the inlet manifold 11.
[0026] Rather than increasing the diameter D of the inlet manifold 11 along its entire longitudinal axis, an alternative design is shown in Fig. 4A wherein the cross-section area of a header 31 is enlarged only in the immediate vicinity of the insertion points of the channels 21, 22 and 23 into the header 31. In this way, the restriction to the refrigerant flow around the ends of the channels is avoided or limited so as to promote favorable uniform conditions to the refrigerant flow into the channels, as desired. Although the form and shape of the enlargements may vary, the wavy shape tends to provide a smoother, less disturbed motion of the refrigerant passing along the inlet header and would be preferred.
[0027] Alternatively, as shown in Fig. 4B and 4C, an inlet manifold can be made of an oval or rectangular shape as shown by 37 and 38 respectively, without appreciably increasing its overall cross-section area. This will prevent refrigerant flow velocity reduction and potential undesired phase separation. [0028] Furthermore, as shown in Fig. 5, a similar technique can be applied to the outlet manifold 41, with the downstream channels having higher insertion depths. Although the outlet manifold (typically having a single phase refrigerant vapor) has a less pronounced influence on the refrigerant distribution among the channels, such balancing of the flow impedances will further assist in the maldistribution problem resolution.
[0029] Furthermore, it should be noted that both vertical and horizontal channel orientations will take advantage from the teaching of the present invention, although higher benefits will be obtained for the latter configuration. Also, although the teachings of this invention are particularly advantageous for the evaporator applications, refrigerant system condensers may benefit from them as well. [0030] While the present invention has been particularly shown and described with reference to preferred and alternate embodiments as illustrated in the drawings, it will be understood by one skilled in the art that various changes in detail may be effected therein without departing from the true spirit and scope of the invention as defined by the claims.

Claims

We Claim:
1. A parallel flow heat exchanger comprising: an inlet manifold having an inlet opening for conducting the flow of fluid into said inlet manifold and a plurality of outlet openings for conducting the flow of fluid from said inlet manifold; a plurality of channels aligned in a substantially parallel relationship and fluidly connected to said plurality of outlet openings for conducting the flow of fluid from said inlet manifold; an outlet manifold fluidly connected to said plurality of channels for receiving the flow of fluid therefrom; wherein said plurality of channels extend into said inlet manifold at varying depths.
2. A parallel flow heat exchanger as set forth in claim 1, wherein the depths of extension into said inlet manifold for said plurality of channels decrease toward the downstream end of the inlet manifold.
3. A parallel flow heat exchanger as set forth in claim 2, wherein said parallel channels are divided into sections with each section having equal extension depths and the depths of extension into said inlet manifold decreasing from section to section toward the downstream end of the inlet manifold.
4. A parallel flow heat exchanger as set forth in claim 1, wherein said plurality of channels are substantially flat in planes transverse to the longitudinal axis of the inlet manifold and further wherein the cross-section areas of said inlet manifold are locally enlarged in the vicinities of those areas surrounding said flat channels to allow for the flow of refrigerant around said plurality of channels.
5. A parallel flow heat exchanger as set forth in claim 1 , wherein said plurality of channels are substantially flat in planes transverse to the longitudinal axis of the inlet manifold and further wherein the cross-section area of said inlet manifold is of an oval shape.
6. A parallel flow heat exchanger as set forth in claim 1, wherein said plurality of channels is substantially flat in a direction transverse to the longitudinal axis of the inlet manifold and further wherein the cross-section area of said inlet manifold is of a rectangular shape.
7. A parallel flow heat exchanger as set forth in claim 1 wherein said plurality of channels extend into said outlet manifold at varying depths.
8. A parallel flow heat exchanger of the type having an inlet manifold fluidly interconnected to an outlet manifold by a plurality of parallel channels for conducting the flow of a fluid therethrough and adapted for having a second fluid circulated thereover for purposes of exchange of heat between the two fluids; wherein said plurality of parallel channels extend into said inlet manifold at varying depths.
9. A parallel flow heat exchanger as set forth in claim 8, wherein the depths of extension into said inlet manifold for said plurality of channels decrease toward the downstream end of the inlet manifold.
10. A parallel flow heat exchanger as set forth in claim 9, wherein said parallel channels are divided into sections with each section having equal extension depths and the depths of extension into said inlet manifold decreasing from section to section toward the downstream end of the inlet manifold.
11. A parallel flow heat exchanger as set forth in claim 8, wherein said plurality of channels are substantially flat in planes transverse to the longitudinal axis of the inlet manifold and further wherein the cross-section areas of said inlet manifold are locally enlarged in1 the vicinities of those areas surrounding said flat channels to allow for the flow of refrigerant around said plurality of channels.
12. A parallel flow heat exchanger as set forth in claim 8, wherein said plurality of channels is substantially flat in a direction transverse to the longitudinal axis of the inlet manifold and further wherein the cross-section area of said inlet manifold is of an oval shape.
13. A parallel flow heat exchanger as set forth in claim 8, wherein said plurality of channels is substantially flat in a direction transverse to the longitudinal axis of the inlet manifold and further wherein the cross-section area of said inlet manifold is of a rectangular shape.
14. A parallel flow heat exchanger as set forth in claim 8 wherein said plurality of parallel channels extend into said outlet manifold at varying depths.
EP05817473.1A 2004-11-12 2005-11-04 Parallel flow evaporator with variable channel insertion depth Expired - Lifetime EP1809958B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US10/987,960 US20060101849A1 (en) 2004-11-12 2004-11-12 Parallel flow evaporator with variable channel insertion depth
PCT/US2005/040164 WO2006055297A2 (en) 2004-11-12 2005-11-04 Parallel flow evaporator with variable channel insertion depth

Publications (3)

Publication Number Publication Date
EP1809958A2 true EP1809958A2 (en) 2007-07-25
EP1809958A4 EP1809958A4 (en) 2010-11-24
EP1809958B1 EP1809958B1 (en) 2018-01-03

Family

ID=36384714

Family Applications (1)

Application Number Title Priority Date Filing Date
EP05817473.1A Expired - Lifetime EP1809958B1 (en) 2004-11-12 2005-11-04 Parallel flow evaporator with variable channel insertion depth

Country Status (4)

Country Link
US (1) US20060101849A1 (en)
EP (1) EP1809958B1 (en)
ES (1) ES2657624T3 (en)
WO (1) WO2006055297A2 (en)

Families Citing this family (28)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20070119580A1 (en) * 2005-11-25 2007-05-31 Markus Wawzyniak Heat exchanger
WO2008064219A1 (en) * 2006-11-22 2008-05-29 Johnson Controls Technology Company Multichannel evaporator with flow mixing manifold
WO2008083220A1 (en) * 2006-12-27 2008-07-10 Johnson Controls Technology Company Condenser refrigerant distribution
CN101772687B (en) * 2007-06-01 2011-11-16 开利公司 Parallel flow heat exchanger with connectors
US8166776B2 (en) * 2007-07-27 2012-05-01 Johnson Controls Technology Company Multichannel heat exchanger
US8695375B2 (en) * 2008-05-05 2014-04-15 Carrier Corporation Microchannel heat exchanger including multiple fluid circuits
US20110127023A1 (en) * 2008-07-10 2011-06-02 Taras Michael F Design characteristics for heat exchangers distribution insert
US20100006276A1 (en) * 2008-07-11 2010-01-14 Johnson Controls Technology Company Multichannel Heat Exchanger
US8234881B2 (en) 2008-08-28 2012-08-07 Johnson Controls Technology Company Multichannel heat exchanger with dissimilar flow
US8439104B2 (en) * 2009-10-16 2013-05-14 Johnson Controls Technology Company Multichannel heat exchanger with improved flow distribution
DE102010061768A1 (en) * 2010-11-23 2012-05-24 Behr Gmbh & Co. Kg Device for cooling a heat source of a motor vehicle
GB2505829B (en) * 2011-06-24 2017-12-27 Mitsubishi Electric Corp Plate heat exchanger and refrigeration cycle apparatus
WO2013004276A1 (en) * 2011-07-01 2013-01-10 Statoil Petroleum As Multi-phase distribution system, sub sea heat exchanger and a method of temperature control for hydrocarbons
US20130199288A1 (en) * 2012-02-02 2013-08-08 Visteon Global Technologies, Inc. Fluid flow distribution device
US9527261B1 (en) 2012-09-14 2016-12-27 Hrl Laboratories, Llc Hollow polymer micro-truss structures containing pressurized fluids
US20140251585A1 (en) 2013-03-05 2014-09-11 The Boeing Company Micro-lattice Cross-flow Heat Exchangers for Aircraft
JP6183100B2 (en) * 2013-09-25 2017-08-23 株式会社デンソー Cold storage heat exchanger
US9783324B2 (en) 2014-08-26 2017-10-10 The Boeing Company Vessel insulation assembly
CN104764255A (en) * 2015-03-26 2015-07-08 广东美的制冷设备有限公司 Parallel flow heat exchanger
US20170045309A1 (en) * 2015-08-11 2017-02-16 Hamilton Sundstrand Corporation High temperature flow manifold
US9816767B2 (en) * 2016-01-12 2017-11-14 Hamilton Sundstrand Corporation Tubes and manifolds for heat exchangers
US20190234626A1 (en) * 2016-09-12 2019-08-01 Mitsubishi Electric Corporation Header, heat exchanger, and air-conditioning apparatus
US10179428B2 (en) 2016-11-17 2019-01-15 The Boeing Company Mechanically reinforced foam insulation panel and methods of making the same
WO2018173256A1 (en) * 2017-03-24 2018-09-27 三菱電機株式会社 Air conditioning device
CN108286823A (en) * 2018-01-31 2018-07-17 李春花 A kind of evenly distributed solar water heater
CN108253640A (en) * 2018-01-31 2018-07-06 李春花 A kind of special-shaped solar water heater
DE102021213378A1 (en) 2021-11-26 2023-06-01 Mahle International Gmbh capacitor
WO2025063267A1 (en) * 2023-09-21 2025-03-27 三菱重工サーマルシステムズ株式会社 Heat exchanger

Family Cites Families (25)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR1291617A (en) * 1961-03-13 1962-04-27 Const Mecaniques Et Aeronautiq Improvements to automobile radiators
FR2417732A1 (en) * 1978-02-20 1979-09-14 Cem Comp Electro Mec PROCESS FOR PROVIDING OR REMOVING HEAT TO A CONDENSABLE FLUID
US4382468A (en) * 1979-05-17 1983-05-10 Hastwell P J Flat plate heat exchanger modules
DE3914773C2 (en) * 1989-05-05 1994-03-03 Mtu Muenchen Gmbh Heat exchanger with at least two header pipes
JPH0737865B2 (en) * 1989-06-28 1995-04-26 松下電器産業株式会社 Shunt
JP2801373B2 (en) * 1990-07-02 1998-09-21 サンデン株式会社 Heat exchanger
FR2690235A1 (en) * 1992-04-16 1993-10-22 Valeo Thermique Moteur Sa Tubular box wall of fluid and method for the manufacture of a heat exchanger by driving of circulation tubes.
JPH05332693A (en) * 1992-06-02 1993-12-14 Showa Alum Corp Heat exchanger
JPH08136182A (en) * 1994-11-11 1996-05-31 Toshiba Corp Heat exchanger
KR0165067B1 (en) * 1996-04-09 1999-01-15 구자홍 2-row flat tube heat exchanger
JPH1089883A (en) * 1996-09-17 1998-04-10 Zexel Corp Header pipe for heat exchanger and manufacturing device therefor
US5881456A (en) * 1997-03-20 1999-03-16 Arup Alu-Rohr Und Profil Gmbh Header tubes for heat exchangers and the methods used for their manufacture
DE19719261C2 (en) * 1997-05-07 2001-06-07 Valeo Klimatech Gmbh & Co Kg Double-flow flat tube evaporator of a motor vehicle air conditioning system
US5941303A (en) * 1997-11-04 1999-08-24 Thermal Components Extruded manifold with multiple passages and cross-counterflow heat exchanger incorporating same
DE19918616C2 (en) * 1998-10-27 2001-10-31 Valeo Klimatechnik Gmbh Condenser for condensing the internal refrigerant of an automotive air conditioning system
FR2786259B1 (en) * 1998-11-20 2001-02-02 Valeo Thermique Moteur Sa COMBINED HEAT EXCHANGER, PARTICULARLY FOR A MOTOR VEHICLE
US6155339A (en) * 1999-06-18 2000-12-05 Grapengater; Richard B. Obround header for a heat exchanger
JP2001124486A (en) * 1999-10-25 2001-05-11 Denso Corp Heat exchanger
US6988539B2 (en) * 2000-01-07 2006-01-24 Zexel Valeo Climate Control Corporation Heat exchanger
JP2001304775A (en) * 2000-04-26 2001-10-31 Mitsubishi Heavy Ind Ltd Air conditioner for vehicle
JP2002031436A (en) * 2000-05-09 2002-01-31 Sanden Corp Sub-cooling type condenser
JP2002130988A (en) * 2000-10-20 2002-05-09 Mitsubishi Heavy Ind Ltd Laminated heat-exchanger
JP2002139290A (en) * 2000-10-31 2002-05-17 Toyo Radiator Co Ltd Module type heat exchanger and manufacturing method thereof
US6523260B2 (en) * 2001-07-05 2003-02-25 Harsco Technologies Corporation Method of making a seamless unitary body quadrilateral header for heat exchanger
KR100493694B1 (en) * 2002-12-11 2005-06-02 엘지전자 주식회사 Micro Channel Heat Exchanger

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO2006055297A3 *

Also Published As

Publication number Publication date
EP1809958B1 (en) 2018-01-03
WO2006055297A2 (en) 2006-05-26
EP1809958A4 (en) 2010-11-24
WO2006055297A3 (en) 2006-12-07
US20060101849A1 (en) 2006-05-18
ES2657624T3 (en) 2018-03-06

Similar Documents

Publication Publication Date Title
EP1809958B1 (en) Parallel flow evaporator with variable channel insertion depth
US8302673B2 (en) Parallel flow evaporator with spiral inlet manifold
US8171987B2 (en) Minichannel heat exchanger header insert for distribution
US7398819B2 (en) Minichannel heat exchanger with restrictive inserts
US20100071392A1 (en) Parallel flow evaporator with shaped manifolds
EP1844290B1 (en) Parallel flow heat exchangers incorporating porous inserts
US20080105420A1 (en) Parallel Flow Heat Exchanger With Crimped Channel Entrance
US20080104975A1 (en) Liquid-Vapor Separator For A Minichannel Heat Exchanger
US7163052B2 (en) Parallel flow evaporator with non-uniform characteristics
US8333088B2 (en) Heat exchanger design for improved performance and manufacturability
US20100170664A1 (en) Parallel flow heat exchanger with connectors
HK1138637B (en) Minichannel heat exchanger header insert for distribution
HK1132792A (en) Parallel flow heat exchanger with crimped channel entrance

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

17P Request for examination filed

Effective date: 20070507

AK Designated contracting states

Kind code of ref document: A2

Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HU IE IS IT LI LT LU LV MC NL PL PT RO SE SI SK TR

DAX Request for extension of the european patent (deleted)
A4 Supplementary search report drawn up and despatched

Effective date: 20101022

17Q First examination report despatched

Effective date: 20160411

GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: GRANT OF PATENT IS INTENDED

INTG Intention to grant announced

Effective date: 20170630

GRAS Grant fee paid

Free format text: ORIGINAL CODE: EPIDOSNIGR3

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: THE PATENT HAS BEEN GRANTED

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HU IE IS IT LI LT LU LV MC NL PL PT RO SE SI SK TR

REG Reference to a national code

Ref country code: GB

Ref legal event code: FG4D

REG Reference to a national code

Ref country code: CH

Ref legal event code: EP

Ref country code: AT

Ref legal event code: REF

Ref document number: 960664

Country of ref document: AT

Kind code of ref document: T

Effective date: 20180115

REG Reference to a national code

Ref country code: NL

Ref legal event code: FP

Ref country code: IE

Ref legal event code: FG4D

REG Reference to a national code

Ref country code: DE

Ref legal event code: R096

Ref document number: 602005053324

Country of ref document: DE

REG Reference to a national code

Ref country code: ES

Ref legal event code: FG2A

Ref document number: 2657624

Country of ref document: ES

Kind code of ref document: T3

Effective date: 20180306

REG Reference to a national code

Ref country code: LT

Ref legal event code: MG4D

REG Reference to a national code

Ref country code: AT

Ref legal event code: MK05

Ref document number: 960664

Country of ref document: AT

Kind code of ref document: T

Effective date: 20180103

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: FI

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180103

Ref country code: LT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180103

Ref country code: CY

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180103

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: BG

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180403

Ref country code: IS

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180503

Ref country code: GR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180404

Ref country code: PL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180103

Ref country code: LV

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180103

Ref country code: SE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180103

Ref country code: AT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180103

REG Reference to a national code

Ref country code: DE

Ref legal event code: R097

Ref document number: 602005053324

Country of ref document: DE

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: EE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180103

Ref country code: IT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180103

Ref country code: RO

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180103

PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: CZ

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180103

Ref country code: DK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180103

Ref country code: SK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180103

26N No opposition filed

Effective date: 20181005

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SI

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180103

REG Reference to a national code

Ref country code: DE

Ref legal event code: R119

Ref document number: 602005053324

Country of ref document: DE

REG Reference to a national code

Ref country code: CH

Ref legal event code: PL

REG Reference to a national code

Ref country code: NL

Ref legal event code: MM

Effective date: 20181201

GBPC Gb: european patent ceased through non-payment of renewal fee

Effective date: 20181104

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: LU

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20181104

Ref country code: MC

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180103

REG Reference to a national code

Ref country code: BE

Ref legal event code: MM

Effective date: 20181130

REG Reference to a national code

Ref country code: IE

Ref legal event code: MM4A

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: NL

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20181201

Ref country code: LI

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20181130

Ref country code: CH

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20181130

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: FR

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20181130

Ref country code: DE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20190601

Ref country code: IE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20181104

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: BE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20181130

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: GB

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20181104

REG Reference to a national code

Ref country code: ES

Ref legal event code: FD2A

Effective date: 20200102

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: ES

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20181105

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: TR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180103

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: PT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180103

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: HU

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT; INVALID AB INITIO

Effective date: 20051104