EP2242963A1 - Heat exchanger including multiple tube distributor - Google Patents

Heat exchanger including multiple tube distributor

Info

Publication number
EP2242963A1
EP2242963A1 EP08732511A EP08732511A EP2242963A1 EP 2242963 A1 EP2242963 A1 EP 2242963A1 EP 08732511 A EP08732511 A EP 08732511A EP 08732511 A EP08732511 A EP 08732511A EP 2242963 A1 EP2242963 A1 EP 2242963A1
Authority
EP
European Patent Office
Prior art keywords
tube
recited
heat exchanger
orifices
fluid
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
EP08732511A
Other languages
German (de)
French (fr)
Other versions
EP2242963B1 (en
Inventor
Robert Hong-Leung Chiang
Pingli Hou
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 EP2242963A1 publication Critical patent/EP2242963A1/en
Application granted granted Critical
Publication of EP2242963B1 publication Critical patent/EP2242963B1/en
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/02—Tubular elements of cross-section which is non-circular
    • F28F1/022—Tubular elements of cross-section which is non-circular with multiple channels
    • 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
    • F25B39/02—Evaporators
    • F25B39/028—Evaporators having distributing means
    • 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
    • F28F9/027—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits in the form of distribution pipes
    • F28F9/0273—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits in the form of distribution pipes with multiple holes
    • 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
    • F25B39/02—Evaporators
    • F25B39/022—Evaporators with plate-like or laminated elements

Definitions

  • This invention relates generally to a microchannel heat exchanger including an inlet manifold and a distributor tube.
  • a microchannel heat exchanger (MCHX) includes flat tubes that extend between an inlet manifold and an outlet manifold. Refrigerant flows through the flat tubes and exchanges heat with air that passes over the tubes.
  • a distributor tube can be used to decrease maldistribution of the refrigerant in the inlet manifold.
  • the distributor tube includes an inlet, an outlet and orifices.
  • Refrigerant enters the tube through the inlet, and the outlet is blocked to discharge the refrigerant through the orifices.
  • the build-up of pressure in the distributor tube causes the refrigerant to equally distribute along the length of the distributor tube.
  • the orifices are appropriately sized to cause a pressure drop or build-up in the distributor tube.
  • the distributor tube and the orifices are also sized appropriately to reduce the amount of separation of vapor refrigerant and liquid refrigerant in the two-phase refrigerant flow.
  • the inlet manifold is long (such as greater than 800mm)
  • the pressure drop along the length of the distributor tube will be uneven, and the refrigerant will not equally distribute along the length of the distributor tube.
  • Exemplary embodiments of the invention include a heat exchanger including tubes and an inlet manifold to direct a first fluid into the tubes at a third direction.
  • the heat exchanger also includes a distributor tube located within the inlet manifold.
  • the distributor tube includes a short tube including a plurality of first orifices that direct the first fluid into the inlet manifold at a first direction, and a long tube including a plurality of second orifices that direct the first fluid into the inlet manifold at a second direction.
  • Further exemplary embodiments include a refrigerant system including a compressor for compressing a refrigerant, a condenser for cooling the refrigerant, an expansion device for expanding the refrigerant, and a microchannel evaporator for heating the refrigerant.
  • the microchannel evaporator includes tubes, an inlet manifold to direct the refrigerant into the tubes at a third direction, and a distributor tube located within the inlet manifold.
  • the distributor tube includes a short tube including a plurality of first orifices that direct the refrigerant into the inlet manifold at a first direction and a long tube including a plurality of second orifices that direct the refrigerant into the inlet manifold at a second direction.
  • Figure 1 illustrates a prior art refrigeration system
  • Figure 2 illustrates a microchannel evaporator
  • Figure 3 illustrates a side view of a distributor tube
  • Figure 4 illustrates a perspective view of an inlet manifold with the distributor tube shown in phantom
  • Figure 5 illustrates a cross-sectional view of the inlet manifold taken along line 5-5 of Figure 4.
  • Figure 1 illustrates a refrigeration system 20 including a compressor 22, a condenser 24, an expansion device 26, and an evaporator 28.
  • Both the condenser 24 and the evaporator 28 are heat exchangers and may be microchannel heat exchangers. In the example shown, the evaporator 28 is the microchannel heat exchanger.
  • Refrigerant circulates through the closed circuit refrigeration system 20.
  • a heat pump 35 can be employed to reverse the flow of the refrigerant through the refrigeration system 20. When the heat pump 35 operates, the evaporator 28 functions as a condenser, and the condenser 24 functions as an evaporator.
  • the refrigerant exits the compressor 22 at a high pressure and a high enthalpy and flows through the condenser 24.
  • the refrigerant rejects heat to air and exits the condenser 24 at a low enthalpy and a high pressure.
  • a fan 30 directs the air through the condenser 24.
  • the cooled refrigerant then passes through the expansion device 26, expanding the refrigerant to a low pressure.
  • the refrigerant flows through the evaporator 28.
  • the refrigerant accepts heat from air, exiting the evaporator 28 at a high enthalpy and a low pressure.
  • a fan 32 blows air through the evaporator 28.
  • the refrigerant then flows to the compressor 22, completing the cycle.
  • FIG. 2 shows the evaporator 28.
  • the evaporator 28 includes an inlet manifold 40 and an outlet manifold 42 that extend along an axis X.
  • the inlet manifold 40 includes a body portion 43 and openings 41 and has a length d.
  • a plurality of flat tubes 44 having a length c extend between the manifolds 40 and 42 along an axis Y.
  • the axis X is substantially perpendicular to the axis Y.
  • Each of the openings 41 of the inlet manifold 40 aligns with one of the flat tubes 44. Refrigerant from the expansion device 26 flows into the inlet manifold 40.
  • the refrigerant from the inlet manifold 40 flows through the openings 41, into the plurality of flat tubes 44 and accepts heat from air 46 flowing over the flat tubes 44.
  • the evaporator 28 can also include a plurality of fins 48 having louvers positioned between the flat tubes 44 to aid in heat transfer between the refrigerant and the air.
  • the refrigerant then flows into the outlet manifold 42 through openings 45 and is directed to the compressor 22 through an outlet opening 70.
  • a distributor tube 34 including a short tube 34a and a long tube 34b is located in the body portion 43 of the inlet manifold 40.
  • a y- shaped flow splitter 52 is attached to the distributor tube 34.
  • the flow splitter 52 includes an inlet portion 56 and two parallel outlet portions 54a and 54b.
  • An inlet tube 50 is in fluid communication with the inlet portion 52, and the short tube 34a and the long tube 34b are in fluid communication with the outlet portions 54a and 54b, respectively.
  • the tubes 34a and 34b are parallel to each other and to the inlet tube 50.
  • the tube 34a includes a first end 62a connected to the outlet portion 54a of the flow splitter 52 and an opposing second end 64a that is blocked by a stop 60a.
  • the tube 34b includes a first end 62b connected to the outlet portion 54b of the flow splitter 52 and an opposing second end 64b that is blocked by a stop 60b.
  • the short tube 34a has a first length a
  • the long tube 34b has a second length b. That is, the first length a is less than the second length b.
  • the first length a of the short tube 34a is approximately 30-70% of the second length b of the long tube 34b, considering the pressure balance within the tubes 34a and 34b.
  • the second length b of the long tube 34b is approximately equal to the length d of the inlet manifold 40.
  • the second length b of the long tube 34b can be slightly less than the length d of the inlet manifold 40, such as approximately 94 to 100% of the length d of the inlet manifold 40.
  • the second end 64a of the short tube 34a aligned with a location 71 of the long tube 34b. That is, the location 71 on the long tube 34b is substantially between the ends 62b and 64b of the long tube 34b. In one example, the location 71 is substantially in the middle of the ends 62b and 64b.
  • the tubes 34a and 34b each include orifices 58a and 58b, respectively.
  • the orifices 58a and 58b are appropriately sized to cause a pressure drop or a pressure build-up in the distributor tube 34 and to reduce the separation of vapor refrigerant and liquid refrigerant in the two-phase refrigerant flow.
  • the orifices 58a of the short tube 34a are linearly aligned and are located in a section 75 defined between the ends 62a and 64a of the short tube 34a.
  • the orifices 58b of the long tube 34b are linearly aligned and are located in a section 73 defined between the location 71 and the end 64b of the long tube 34b.
  • the orifices 58a and 58b are located in different sections 73 and 75 of the distributor tube 34.
  • the orifices 58a and 58b are aligned such that they extend along a straight line substantially parallel to the lengths a and b of the tubes 34a and 34b, respectively.
  • the orifices 58a direct refrigerant flowing through the short tube 34a into the inlet manifold 40 at a first direction E
  • the orifices 58b direct refrigerant flowing through the long tube 34b into the inlet manifold 40 at a second direction F.
  • the refrigerant directed into the inlet manifold 40 is then directed through the openings 41 and into one of the flat tubes 44 for heat exchange with the air at a third direction G.
  • first direction E and the second direction F are oriented at an angle relative to the third direction G.
  • first direction E and the second direction F can be oriented at an angle that is approximately 45° to 315° clockwise from the third direction G.
  • the orifices 58a and 58b can be located at any number of locations and are located in a way that helps to induce and cause additional mixing when the refrigerant is discharged from the tubes 34a and 34b.
  • the second direction F is approximately 135° clockwise relative to the third direction G
  • the first direction E is approximately 225° clockwise (or 135° counter-clockwise) relative to the third direction G.
  • the refrigerant exiting the expansion device 26 is in two phases and includes approximately 80% vapor and approximately 20% liquid by mass.
  • the density of the liquid refrigerant is approximately 10-100 times greater than the density of the vapor refrigerant. Therefore, the vapor refrigerant flows faster than the liquid refrigerant.
  • Refrigerant from the expansion device 26 enters the distributor tube 34 through the inlet tube 50 and flows into the tubes 34a and 34b.
  • the flow splitter 52 divides the refrigerant entering the inlet manifold 40 such that approximately 50% enters the short tube 34a and approximately 50% enters the long tube 34b. As the second ends 64a and 64b of the tubes 34a and 34b, respectively, are blocked by the stops 60a and 60b, respectively, the refrigerant is forced through the orifices 58a and 58b and into the inlet manifold 40. The increase in pressure causes the refrigerant to distribute equally along the length d of the inlet manifold 40.
  • the refrigerant entering the short tube 34a is equally distributed to the section 75 through the orifices 58a, and the refrigerant entering the long tube 34b is equally distributed to the section 73 through the orifices 58b.
  • the refrigerant is equally distributed to each section 73 and 75 as half of the refrigerant is provided to each tube 34a and 34b.
  • An equal distribution of refrigerant is possible as half of the refrigerant is provided to each half of the length d of the inlet manifold 40 for distribution to the flat tubes 44.
  • As a portion of the refrigerant is specifically designated for distribution to a specific section 73 and 75 of the inlet manifold 40, a better distribution of refrigerant is possible in each section 73 and 75 of the inlet manifold 40.
  • the length d of the inlet manifold 40 is very long, such as greater than 800 mm.
  • the length d of the inlet manifold 40 is 800 mm
  • half of the refrigerant would be designated to each 400 mm section of the inlet manifold 40, providing a more even distribution of refrigerant in each 400 mm section, as each 400 mm section is designated to receive half of the refrigerant.

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)

Abstract

A heat exchanger includes tubes and an inlet manifold to direct a first fluid into the tubes at a third direction. Heat is exchanged between the first fluid and a second fluid in the tubes. The heat exchanger also includes a distributor tube located within the inlet manifold. The distributor tube includes a short tube including a plurality of first orifices that direct the first fluid into the inlet manifold at a first direction, and a long tube including a plurality of second orifices that direct the first fluid into the inlet manifold at a second direction.

Description

HEAT EXCHANGER INCLUDING MULTIPLE TUBE DISTRIBUTOR
BACKGROUND OF THE INVENTION
This invention relates generally to a microchannel heat exchanger including an inlet manifold and a distributor tube.
A microchannel heat exchanger (MCHX) includes flat tubes that extend between an inlet manifold and an outlet manifold. Refrigerant flows through the flat tubes and exchanges heat with air that passes over the tubes.
Maldistribution of two-phase refrigerant in the flat tubes can be a problem. A distributor tube can be used to decrease maldistribution of the refrigerant in the inlet manifold. The distributor tube includes an inlet, an outlet and orifices.
Refrigerant enters the tube through the inlet, and the outlet is blocked to discharge the refrigerant through the orifices. The build-up of pressure in the distributor tube causes the refrigerant to equally distribute along the length of the distributor tube. The orifices are appropriately sized to cause a pressure drop or build-up in the distributor tube. The distributor tube and the orifices are also sized appropriately to reduce the amount of separation of vapor refrigerant and liquid refrigerant in the two-phase refrigerant flow.
However, when the inlet manifold is long (such as greater than 800mm), the pressure drop along the length of the distributor tube will be uneven, and the refrigerant will not equally distribute along the length of the distributor tube.
SUMMARY OF THE INVENTION
Exemplary embodiments of the invention include a heat exchanger including tubes and an inlet manifold to direct a first fluid into the tubes at a third direction.
Heat is exchanged between the first fluid and a second fluid in the tubes. The heat exchanger also includes a distributor tube located within the inlet manifold. The distributor tube includes a short tube including a plurality of first orifices that direct the first fluid into the inlet manifold at a first direction, and a long tube including a plurality of second orifices that direct the first fluid into the inlet manifold at a second direction. Further exemplary embodiments include a refrigerant system including a compressor for compressing a refrigerant, a condenser for cooling the refrigerant, an expansion device for expanding the refrigerant, and a microchannel evaporator for heating the refrigerant. The microchannel evaporator includes tubes, an inlet manifold to direct the refrigerant into the tubes at a third direction, and a distributor tube located within the inlet manifold. The distributor tube includes a short tube including a plurality of first orifices that direct the refrigerant into the inlet manifold at a first direction and a long tube including a plurality of second orifices that direct the refrigerant into the inlet manifold at a second direction. These and other features of the present invention will be best understood from the following specification and drawings.
BRIEF DESCRIPTION OF THE DRAWINGS
The various features and advantages of the invention will become apparent to those skilled in the art from the following detailed description of the currently preferred embodiment. The drawings that accompany the detailed description can be briefly described as follows:
Figure 1 illustrates a prior art refrigeration system; Figure 2 illustrates a microchannel evaporator; Figure 3 illustrates a side view of a distributor tube;
Figure 4 illustrates a perspective view of an inlet manifold with the distributor tube shown in phantom; and
Figure 5 illustrates a cross-sectional view of the inlet manifold taken along line 5-5 of Figure 4.
DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS
Figure 1 illustrates a refrigeration system 20 including a compressor 22, a condenser 24, an expansion device 26, and an evaporator 28. Both the condenser 24 and the evaporator 28 are heat exchangers and may be microchannel heat exchangers. In the example shown, the evaporator 28 is the microchannel heat exchanger. Refrigerant circulates through the closed circuit refrigeration system 20. A heat pump 35 can be employed to reverse the flow of the refrigerant through the refrigeration system 20. When the heat pump 35 operates, the evaporator 28 functions as a condenser, and the condenser 24 functions as an evaporator. The refrigerant exits the compressor 22 at a high pressure and a high enthalpy and flows through the condenser 24. In the condenser 24, the refrigerant rejects heat to air and exits the condenser 24 at a low enthalpy and a high pressure. A fan 30 directs the air through the condenser 24. The cooled refrigerant then passes through the expansion device 26, expanding the refrigerant to a low pressure. After expansion, the refrigerant flows through the evaporator 28. In the evaporator 28, the refrigerant accepts heat from air, exiting the evaporator 28 at a high enthalpy and a low pressure. A fan 32 blows air through the evaporator 28. The refrigerant then flows to the compressor 22, completing the cycle.
Figure 2 shows the evaporator 28. The evaporator 28 includes an inlet manifold 40 and an outlet manifold 42 that extend along an axis X. The inlet manifold 40 includes a body portion 43 and openings 41 and has a length d. A plurality of flat tubes 44 having a length c extend between the manifolds 40 and 42 along an axis Y. The axis X is substantially perpendicular to the axis Y. Each of the openings 41 of the inlet manifold 40 aligns with one of the flat tubes 44. Refrigerant from the expansion device 26 flows into the inlet manifold 40.
The refrigerant from the inlet manifold 40 flows through the openings 41, into the plurality of flat tubes 44 and accepts heat from air 46 flowing over the flat tubes 44. The evaporator 28 can also include a plurality of fins 48 having louvers positioned between the flat tubes 44 to aid in heat transfer between the refrigerant and the air. The refrigerant then flows into the outlet manifold 42 through openings 45 and is directed to the compressor 22 through an outlet opening 70.
As shown in Figures 3 and 4, a distributor tube 34 including a short tube 34a and a long tube 34b is located in the body portion 43 of the inlet manifold 40. A y- shaped flow splitter 52 is attached to the distributor tube 34. The flow splitter 52 includes an inlet portion 56 and two parallel outlet portions 54a and 54b. An inlet tube 50 is in fluid communication with the inlet portion 52, and the short tube 34a and the long tube 34b are in fluid communication with the outlet portions 54a and 54b, respectively. In one example, the tubes 34a and 34b are parallel to each other and to the inlet tube 50.
The tube 34a includes a first end 62a connected to the outlet portion 54a of the flow splitter 52 and an opposing second end 64a that is blocked by a stop 60a. The tube 34b includes a first end 62b connected to the outlet portion 54b of the flow splitter 52 and an opposing second end 64b that is blocked by a stop 60b. The short tube 34a has a first length a, and the long tube 34b has a second length b. That is, the first length a is less than the second length b. The first length a of the short tube 34a is approximately 30-70% of the second length b of the long tube 34b, considering the pressure balance within the tubes 34a and 34b.
In one example, the second length b of the long tube 34b is approximately equal to the length d of the inlet manifold 40. However, the second length b of the long tube 34b can be slightly less than the length d of the inlet manifold 40, such as approximately 94 to 100% of the length d of the inlet manifold 40. The second end 64a of the short tube 34a aligned with a location 71 of the long tube 34b. That is, the location 71 on the long tube 34b is substantially between the ends 62b and 64b of the long tube 34b. In one example, the location 71 is substantially in the middle of the ends 62b and 64b.
The tubes 34a and 34b each include orifices 58a and 58b, respectively. The orifices 58a and 58b are appropriately sized to cause a pressure drop or a pressure build-up in the distributor tube 34 and to reduce the separation of vapor refrigerant and liquid refrigerant in the two-phase refrigerant flow. The orifices 58a of the short tube 34a are linearly aligned and are located in a section 75 defined between the ends 62a and 64a of the short tube 34a. The orifices 58b of the long tube 34b are linearly aligned and are located in a section 73 defined between the location 71 and the end 64b of the long tube 34b. Therefore, the orifices 58a and 58b are located in different sections 73 and 75 of the distributor tube 34. The orifices 58a and 58b are aligned such that they extend along a straight line substantially parallel to the lengths a and b of the tubes 34a and 34b, respectively. As shown in Figure 5, the orifices 58a direct refrigerant flowing through the short tube 34a into the inlet manifold 40 at a first direction E, and the orifices 58b direct refrigerant flowing through the long tube 34b into the inlet manifold 40 at a second direction F. The refrigerant directed into the inlet manifold 40 is then directed through the openings 41 and into one of the flat tubes 44 for heat exchange with the air at a third direction G.
In one example, the first direction E and the second direction F are oriented at an angle relative to the third direction G. In one example, the first direction E and the second direction F can be oriented at an angle that is approximately 45° to 315° clockwise from the third direction G. However, the orifices 58a and 58b can be located at any number of locations and are located in a way that helps to induce and cause additional mixing when the refrigerant is discharged from the tubes 34a and 34b.
In one example shown in Figure 5, the second direction F is approximately 135° clockwise relative to the third direction G, and the first direction E is approximately 225° clockwise (or 135° counter-clockwise) relative to the third direction G. The refrigerant exiting the expansion device 26 is in two phases and includes approximately 80% vapor and approximately 20% liquid by mass. The density of the liquid refrigerant is approximately 10-100 times greater than the density of the vapor refrigerant. Therefore, the vapor refrigerant flows faster than the liquid refrigerant. Refrigerant from the expansion device 26 enters the distributor tube 34 through the inlet tube 50 and flows into the tubes 34a and 34b. The flow splitter 52 divides the refrigerant entering the inlet manifold 40 such that approximately 50% enters the short tube 34a and approximately 50% enters the long tube 34b. As the second ends 64a and 64b of the tubes 34a and 34b, respectively, are blocked by the stops 60a and 60b, respectively, the refrigerant is forced through the orifices 58a and 58b and into the inlet manifold 40. The increase in pressure causes the refrigerant to distribute equally along the length d of the inlet manifold 40.
The refrigerant entering the short tube 34a is equally distributed to the section 75 through the orifices 58a, and the refrigerant entering the long tube 34b is equally distributed to the section 73 through the orifices 58b. The refrigerant is equally distributed to each section 73 and 75 as half of the refrigerant is provided to each tube 34a and 34b. An equal distribution of refrigerant is possible as half of the refrigerant is provided to each half of the length d of the inlet manifold 40 for distribution to the flat tubes 44. As a portion of the refrigerant is specifically designated for distribution to a specific section 73 and 75 of the inlet manifold 40, a better distribution of refrigerant is possible in each section 73 and 75 of the inlet manifold 40.
By employing a short tube 34a and a long tube 34b, maldistribution of the refrigerant can be prevented, especially if the length d of the inlet manifold 40 is very long, such as greater than 800 mm. For example, if the length d of the inlet manifold 40 is 800 mm, half of the refrigerant would be designated to each 400 mm section of the inlet manifold 40, providing a more even distribution of refrigerant in each 400 mm section, as each 400 mm section is designated to receive half of the refrigerant.
The foregoing description is only exemplary of the principles of the invention. Many modifications and variations of the present invention are possible in light of the above teachings. The preferred embodiments of this invention have been disclosed, however, so that one of ordinary skill in the art would recognize that certain modifications would come within the scope of this invention. It is, therefore, to be understood that within the scope of the appended claims, the invention may be practiced otherwise than as specifically described. For that reason the following claims should be studied to determine the true scope and content of this invention.

Claims

1. A heat exchanger comprising: a plurality of tubes, wherein heat is exchanged between a first fluid and a second fluid in the plurality of tubes; an inlet manifold to direct the first fluid into the plurality of tubes at a third direction; and a distributor tube located within the inlet manifold, wherein the distributor tube includes a short tube including a plurality of first orifices that direct the first fluid into the inlet manifold at a first direction and a long tube including a plurality of second orifices that direct the first fluid into the inlet manifold at a second direction.
2. The heat exchanger as recited in claim 1 wherein the heat exchanger is a microchannel evaporator.
3. The heat exchanger as recited in claim 1 wherein the plurality of tubes each include a flattened portion.
4. The heat exchanger as recited in claim 1 wherein the distributor tube includes a flow splitter that directs half of the first fluid into the short tube and the other half of the first fluid into the long tube.
5. The heat exchanger as recited in claim 1 further including an outlet manifold, wherein the plurality of tubes fluidly connect the inlet manifold and the outlet manifold.
6. The heat exchanger as recited in claim 1 wherein the short tube and the long tube are substantially parallel.
7. The heat exchanger as recited in claim 1 wherein the first fluid enters the short tube and the long tube at a first end, and an opposing second end of each of the short tube and the long tube are blocked with a stop.
8. The heat exchanger as recited in claim 1 wherein the first fluid is refrigerant and the second fluid is air, and the refrigerant flows through the plurality of tubes and the air passes over the plurality of tubes.
9. The heat exchanger as recited in claim 1 wherein the plurality of first orifices and the plurality of second orifices are arranged in a linear configuration.
10. The heat exchanger as recited in claim 1 wherein an angle between the first direction and the third direction is substantially equal to another angle between the second direction and the third direction, wherein the first direction is different from the second direction.
11. The heat exchanger as recited in claim 10 wherein the angle and the another angle are each approximately 45° to 315° clockwise from the third direction.
12. The heat exchanger as recited in claim 1 wherein the plurality of first orifices are located in one section of the distributor tube and the plurality of second orifices are located in another section of the distributor tube.
13. The heat exchanger as recited in claim 1 wherein the inlet manifold has a manifold length, the short tube has a short length and the long tube has a long length, wherein the long length is approximately equal to the manifold length, and the short length is approximately 30-70% of the long length.
14. A refrigeration system comprising: a compressor for compressing a refrigerant; a condenser for cooling the refrigerant; an expansion device for expanding the refrigerant; and a microchannel evaporator for heating the refrigerant, wherein the microchannel evaporator includes a plurality of tubes, an inlet manifold to direct the first fluid into the plurality of tubes at a third direction, and a distributor tube located within the inlet manifold, wherein the distributor tube includes a short tube including a plurality of first orifices that direct the first fluid into the inlet manifold at a first direction and a long tube including a plurality of second orifices that direct the first fluid into the inlet manifold at a second direction.
15. The refrigeration system as recited in claim 14 wherein the short tube and the long tube are substantially parallel.
16. The refrigeration system as recited in claim 14 wherein the first fluid enters the short tube and the long tube at a first end, and an opposing second end of each of the short tube and the long tube are blocked with a stop.
17. The refrigeration system as recited in claim 14 wherein the plurality of first orifices and the plurality of second orifices are arranged in a linear configuration.
18. The refrigeration system as recited in claim 14 wherein an angle between the first direction and the third direction is substantially equal to another angle between the second direction and the third direction, wherein the first direction is different from the second direction.
19. The refrigeration system as recited in claim 14 wherein the plurality of first orifices are located in one section of the distributor tube and the plurality of second orifices are located in another section of the distributor tube.
20. The refrigeration system as recited in claim 14 wherein the inlet manifold has a manifold length, the short tube has a short length and the long tube has a long length, wherein the long length is approximately equal to the manifold length, and the short length is approximately 30-70% of the long length.
EP08732511.4A 2008-01-17 2008-03-20 Heat exchanger including multiple tube distributor Not-in-force EP2242963B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CN2008100084270A CN101487669B (en) 2008-01-17 2008-01-17 Heat exchanger comprising multi-pipe distributer
PCT/US2008/057567 WO2009091414A1 (en) 2008-01-17 2008-03-20 Heat exchanger including multiple tube distributor

Publications (2)

Publication Number Publication Date
EP2242963A1 true EP2242963A1 (en) 2010-10-27
EP2242963B1 EP2242963B1 (en) 2015-09-30

Family

ID=39765247

Family Applications (1)

Application Number Title Priority Date Filing Date
EP08732511.4A Not-in-force EP2242963B1 (en) 2008-01-17 2008-03-20 Heat exchanger including multiple tube distributor

Country Status (6)

Country Link
US (1) US20110203308A1 (en)
EP (1) EP2242963B1 (en)
CN (1) CN101487669B (en)
DK (1) DK2242963T3 (en)
ES (1) ES2549120T3 (en)
WO (1) WO2009091414A1 (en)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN112484346A (en) * 2020-12-24 2021-03-12 无锡市同力空调设备有限公司 Refrigerant distributor and dry evaporator with built-in refrigerant distributor
LU101389B1 (en) * 2019-09-12 2021-03-19 Ht Holding Luxembourg S A Heat exchanger for a vehicle

Families Citing this family (37)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR20110104667A (en) * 2010-03-17 2011-09-23 엘지전자 주식회사 Refrigerant distributor, evaporator and refrigeration unit having the refrigerant distributor
CN102072684B (en) * 2011-01-06 2012-10-17 三花控股集团有限公司 Refrigerant distributing device and heat exchanger with same
JP5796518B2 (en) * 2012-03-06 2015-10-21 株式会社デンソー Refrigerant evaporator
WO2013184522A1 (en) * 2012-06-08 2013-12-12 Modine Manufacturing Company Heat exchanger, and method of distributing refrigerant therein
DE102012217340A1 (en) * 2012-09-25 2014-03-27 Behr Gmbh & Co. Kg Heat exchanger
CN102914100B (en) * 2012-09-27 2015-08-19 广东美的制冷设备有限公司 Coolant distribution device and parallel-flow heat exchanger
CN103776206B (en) * 2012-10-22 2019-03-26 浙江盾安人工环境股份有限公司 a refrigerant distributor
US9746255B2 (en) * 2012-11-16 2017-08-29 Mahle International Gmbh Heat pump heat exchanger having a low pressure drop distribution tube
US20140208784A1 (en) * 2013-01-30 2014-07-31 Visteon Global Technologies, Inc. Refrigeration system with isentropic expansion nozzle
US8763424B1 (en) 2013-09-30 2014-07-01 Heat Pump Technologies, LLC Subcooling heat exchanger adapted for evaporator distribution lines in a refrigeration circuit
WO2015072128A1 (en) * 2013-11-14 2015-05-21 日本電気株式会社 Piping structure, cooling device using same, and refrigerant vapor transport method
CN104048548B (en) * 2014-05-26 2016-01-27 杭州三花微通道换热器有限公司 Adjustable refrigerant distributing device and the heat exchanger with it
US10072900B2 (en) * 2014-09-16 2018-09-11 Mahle International Gmbh Heat exchanger distributor with intersecting streams
CN105526739B (en) * 2014-09-29 2019-06-14 杭州三花研究院有限公司 A kind of heat exchanger
CN105783338B (en) * 2015-01-09 2020-11-06 特灵国际有限公司 Heat exchanger
US10551099B2 (en) 2016-02-04 2020-02-04 Mahle International Gmbh Micro-channel evaporator having compartmentalized distribution
US10578377B2 (en) * 2016-03-31 2020-03-03 Mitsubishi Electric Corporation Heat exchanger and refrigeration cycle apparatus
WO2018000662A1 (en) * 2016-06-28 2018-01-04 海信科龙电器股份有限公司 Refrigerant shunt and refrigeration equipment
CN106123409B (en) * 2016-08-22 2018-09-11 杭州三花微通道换热器有限公司 Refrigerant distributing device and parallel-flow heat exchanger
CN106440861B (en) * 2016-08-30 2018-07-13 杭州三花微通道换热器有限公司 Heat exchanger assembly and refrigeration system with it
FR3059397B1 (en) * 2016-11-30 2019-07-26 Valeo Systemes Thermiques DEVICE FOR DISPENSING A REFRIGERANT FLUID INSIDE TUBES OF A HEAT EXCHANGER CONSISTING OF A REFRIGERANT FLUID CIRCUIT
US10563895B2 (en) 2016-12-07 2020-02-18 Johnson Controls Technology Company Adjustable inlet header for heat exchanger of an HVAC system
EP4246075A3 (en) 2017-05-05 2023-12-06 Carrier Corporation Heat exchanger for heat pump applications
DE102017211529A1 (en) 2017-07-06 2019-01-10 Mahle International Gmbh Insert tube for the inlet channel of a plate heat exchanger
US10760835B2 (en) * 2018-09-05 2020-09-01 Audi Ag Evaporator in a refrigerant circuit E
US10760833B2 (en) * 2018-09-05 2020-09-01 Audi Ag Evaporator in a refrigerant circuit c
US10760834B2 (en) * 2018-09-05 2020-09-01 Audi Ag Evaporator in a refrigerant circuit D
CN112013710A (en) * 2019-05-31 2020-12-01 浙江三花智能控制股份有限公司 Distribution pipe and heat exchanger
WO2021234959A1 (en) * 2020-05-22 2021-11-25 三菱電機株式会社 Refrigerant distributor, heat exchanger, and air conditioner
CN113204817B (en) * 2021-04-26 2024-09-17 东南大学 Design method of geothermal heat exchange system for energy tunnel lining
JP7142806B1 (en) * 2021-10-15 2022-09-27 三菱電機株式会社 Distributors, heat exchangers and heat pump devices
JP7693095B2 (en) * 2022-03-18 2025-06-16 三菱電機株式会社 Outdoor unit of air conditioner and air conditioner
CN116817659A (en) * 2022-05-31 2023-09-29 浙江三花智能控制股份有限公司 Heat Exchanger
US12130097B2 (en) * 2022-09-15 2024-10-29 Hamilton Sundstrand Corporation Crossflow heat exchanger with stacked distribution tubes
CN115682472B (en) * 2022-11-01 2024-09-24 浙江宝丰科技股份有限公司 Evaporation type condenser
CN116147233B (en) * 2023-04-21 2023-06-30 广东美博智能环境设备有限公司 Efficient refrigeration plant heat exchange tube
WO2026029092A1 (en) * 2024-07-31 2026-02-05 三菱電機株式会社 Heat exchanger, device provided with heat pump, and temperature control device

Family Cites Families (25)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2098830A (en) * 1935-11-12 1937-11-09 John J Nesbitt Inc Apparatus for the heating of air
US2650799A (en) * 1950-08-11 1953-09-01 Aerofin Corp Heat exchanger
US3976128A (en) * 1975-06-12 1976-08-24 Ford Motor Company Plate and fin heat exchanger
IL107850A0 (en) * 1992-12-07 1994-04-12 Multistack Int Ltd Improvements in plate heat exchangers
DE59405261D1 (en) * 1993-07-03 1998-03-19 Flitsch E Gmbh & Co PLATE HEAT EXCHANGER WITH REFRIGERANT DISTRIBUTOR
JPH08189725A (en) * 1995-01-05 1996-07-23 Nippondenso Co Ltd Refrigerant evaporator
JP3705859B2 (en) * 1996-03-29 2005-10-12 サンデン株式会社 Heat exchanger with distribution device
DE19719263C2 (en) * 1997-05-07 2002-04-25 Valeo Klimatech Gmbh & Co Kg Flat tube evaporator with vertical longitudinal direction of the flat tubes in motor vehicles
DE19719252C2 (en) * 1997-05-07 2002-10-31 Valeo Klimatech Gmbh & Co Kg Double-flow and single-row brazed flat tube evaporator for a motor vehicle air conditioning system
JP2002130988A (en) * 2000-10-20 2002-05-09 Mitsubishi Heavy Ind Ltd Laminated heat-exchanger
US6729386B1 (en) * 2001-01-22 2004-05-04 Stanley H. Sather Pulp drier coil with improved header
DE10149507A1 (en) * 2001-10-06 2003-04-10 Behr Gmbh & Co Heat exchanger, in particular flat-tube heat exchanger of a motor vehicle
US20030116310A1 (en) * 2001-12-21 2003-06-26 Wittmann Joseph E. Flat tube heat exchanger core with internal fluid supply and suction lines
JP2005513403A (en) * 2001-12-21 2005-05-12 ベール ゲーエムベーハー ウント コー カーゲー Especially heat exchanger for automobile
US6814136B2 (en) * 2002-08-06 2004-11-09 Visteon Global Technologies, Inc. Perforated tube flow distributor
KR20040017920A (en) * 2002-08-22 2004-03-02 엘지전자 주식회사 Condensate drainage of heat exchanger
US6688137B1 (en) * 2002-10-23 2004-02-10 Carrier Corporation Plate heat exchanger with a two-phase flow distributor
CN1611907A (en) * 2003-10-30 2005-05-04 乐金电子(天津)电器有限公司 Collector refrigerant distributing structure
EP1548380A3 (en) * 2003-12-22 2006-10-04 Hussmann Corporation Flat-tube evaporator with micro-distributor
US7086249B2 (en) * 2004-10-01 2006-08-08 Advanced Heat Transfer, Llc Refrigerant distribution device and method
US7806171B2 (en) * 2004-11-12 2010-10-05 Carrier Corporation Parallel flow evaporator with spiral inlet manifold
WO2006083443A2 (en) * 2005-02-02 2006-08-10 Carrier Corporation Parallel flow heat exchangers incorporating porous inserts
MX2007009246A (en) * 2005-02-02 2007-09-04 Carrier Corp INSTRUCTION OF DOUBLE FLOW PIPE AND PROVISION FOR A HEAT PUMP MANIFOLD.
US7967060B2 (en) * 2005-08-18 2011-06-28 Parker-Hannifin Corporation Evaporating heat exchanger
US20070119580A1 (en) * 2005-11-25 2007-05-31 Markus Wawzyniak Heat exchanger

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO2009091414A1 *

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
LU101389B1 (en) * 2019-09-12 2021-03-19 Ht Holding Luxembourg S A Heat exchanger for a vehicle
CN112484346A (en) * 2020-12-24 2021-03-12 无锡市同力空调设备有限公司 Refrigerant distributor and dry evaporator with built-in refrigerant distributor

Also Published As

Publication number Publication date
EP2242963B1 (en) 2015-09-30
WO2009091414A1 (en) 2009-07-23
ES2549120T3 (en) 2015-10-23
CN101487669B (en) 2012-08-22
CN101487669A (en) 2009-07-22
US20110203308A1 (en) 2011-08-25
DK2242963T3 (en) 2015-10-26
HK1149955A1 (en) 2011-10-21

Similar Documents

Publication Publication Date Title
EP2242963B1 (en) Heat exchanger including multiple tube distributor
US8225853B2 (en) Multi-pass heat exchangers having return manifolds with distributing inserts
AU2005326694B2 (en) Tube inset and bi-flow arrangement for a header of a heat pump
EP2291600B1 (en) Refrigeration system comprising a microchannel heat exchanger including multiple fluid circuits
US20060054310A1 (en) Evaporator using micro-channel tubes
US20060054312A1 (en) Evaporator using micro-channel tubes
CN108027223B (en) Laminated header, heat exchanger, and air conditioner
EP2313733A2 (en) Integrated multi-circuit microchannel heat exchanger
EP2504655B1 (en) A heat exchanger with a suction line heat exchanger
US20190024954A1 (en) Heat Exchange System
US20100037652A1 (en) Multi-channel heat exchanger with multi-stage expansion
HK1149955B (en) Heat exchanger including multiple tube distributor
JP2687593B2 (en) Refrigerant condenser
CN223077060U (en) Air conditioner
US20250137738A1 (en) Microchannel heat exchanger
CN121739643A (en) Distributor, heat exchanger and refrigeration cycle device
KR20040038328A (en) Coupling device for regenerator
CN119223043A (en) Heat Exchanger
HK1138362B (en) Multi-pass heat exchangers having return manifolds with distributing inserts
HK1117223B (en) Tube inset and bi-flow arrangement for a header of a heat pump
HK1156098A (en) Microchannel heat exchanger including multiple fluid circuits
HK1106285A1 (en) Heat exchanger with multiple stage fluid expansion in header
HK1106285B (en) Heat exchanger with multiple stage fluid expansion in header
HK1138354B (en) Multi-channel heat exchanger with multi-stage expansion device

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: 20100813

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MT NL NO PL PT RO SE SI SK TR

AX Request for extension of the european patent

Extension state: AL BA MK RS

DAX Request for extension of the european patent (deleted)
REG Reference to a national code

Ref country code: HK

Ref legal event code: DE

Ref document number: 1149955

Country of ref document: HK

GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

INTG Intention to grant announced

Effective date: 20150508

GRAS Grant fee paid

Free format text: ORIGINAL CODE: EPIDOSNIGR3

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

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 HR HU IE IS IT LI LT LU LV MC MT NL NO PL PT RO SE SI SK TR

REG Reference to a national code

Ref country code: CH

Ref legal event code: EP

Ref country code: GB

Ref legal event code: FG4D

REG Reference to a national code

Ref country code: AT

Ref legal event code: REF

Ref document number: 752662

Country of ref document: AT

Kind code of ref document: T

Effective date: 20151015

REG Reference to a national code

Ref country code: IE

Ref legal event code: FG4D

REG Reference to a national code

Ref country code: ES

Ref legal event code: FG2A

Ref document number: 2549120

Country of ref document: ES

Kind code of ref document: T3

Effective date: 20151023

REG Reference to a national code

Ref country code: DK

Ref legal event code: T3

Effective date: 20151020

REG Reference to a national code

Ref country code: DE

Ref legal event code: R096

Ref document number: 602008040402

Country of ref document: DE

REG Reference to a national code

Ref country code: NL

Ref legal event code: FP

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

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: 20150930

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: 20150930

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: 20150930

Ref country code: NO

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: 20151230

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: 20151231

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: 752662

Country of ref document: AT

Kind code of ref document: T

Effective date: 20150930

REG Reference to a national code

Ref country code: FR

Ref legal event code: PLFP

Year of fee payment: 9

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

Ref country code: HR

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: 20150930

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: 20150930

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: 20150930

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: 20150930

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: 20150930

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: 20150930

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: 20160130

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

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: 20150930

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: 20160201

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: 20150930

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: 20150930

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: GB

Payment date: 20160223

Year of fee payment: 9

REG Reference to a national code

Ref country code: DE

Ref legal event code: R097

Ref document number: 602008040402

Country of ref document: DE

PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

REG Reference to a national code

Ref country code: HK

Ref legal event code: GR

Ref document number: 1149955

Country of ref document: HK

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: BE

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

Effective date: 20160331

26N No opposition filed

Effective date: 20160701

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

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: 20150930

Ref country code: LU

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: 20160320

REG Reference to a national code

Ref country code: CH

Ref legal event code: PL

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: 20150930

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: BE

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: 20150930

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

Ref country code: LI

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

Effective date: 20160331

Ref country code: IE

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

Effective date: 20160320

Ref country code: CH

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

Effective date: 20160331

REG Reference to a national code

Ref country code: FR

Ref legal event code: PLFP

Year of fee payment: 10

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: FR

Payment date: 20170221

Year of fee payment: 10

Ref country code: DE

Payment date: 20170222

Year of fee payment: 10

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DK

Payment date: 20170222

Year of fee payment: 10

Ref country code: NL

Payment date: 20170221

Year of fee payment: 10

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: ES

Payment date: 20170222

Year of fee payment: 10

REG Reference to a national code

Ref country code: DE

Ref legal event code: R082

Ref document number: 602008040402

Country of ref document: DE

Representative=s name: SCHMITT-NILSON SCHRAUD WAIBEL WOHLFROM PATENTA, DE

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

Ref country code: MT

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: 20150930

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

Effective date: 20170320

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: 20170320

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

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: 20150930

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: 20080320

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: 20150930

Ref country code: MT

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: 20160331

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: 20150930

REG Reference to a national code

Ref country code: DE

Ref legal event code: R119

Ref document number: 602008040402

Country of ref document: DE

REG Reference to a national code

Ref country code: DK

Ref legal event code: EBP

Effective date: 20180331

REG Reference to a national code

Ref country code: NL

Ref legal event code: MM

Effective date: 20180401

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: 20180401

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

Ref country code: DE

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

Effective date: 20181002

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: 20180331

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

Ref country code: DK

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

Effective date: 20180331

REG Reference to a national code

Ref country code: ES

Ref legal event code: FD2A

Effective date: 20190911

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: 20180321