EP2072936B1 - Einheitlicher Wärmetauscher für Klimakreislauf - Google Patents

Einheitlicher Wärmetauscher für Klimakreislauf Download PDF

Info

Publication number
EP2072936B1
EP2072936B1 EP08171881.9A EP08171881A EP2072936B1 EP 2072936 B1 EP2072936 B1 EP 2072936B1 EP 08171881 A EP08171881 A EP 08171881A EP 2072936 B1 EP2072936 B1 EP 2072936B1
Authority
EP
European Patent Office
Prior art keywords
heat exchange
heat exchanger
expansion device
internal heat
evaporator
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.)
Active
Application number
EP08171881.9A
Other languages
English (en)
French (fr)
Other versions
EP2072936A1 (de
Inventor
Stefan Karl
Rody El Chammas
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.)
Valeo Systemes Thermiques SAS
Original Assignee
Valeo Systemes Thermiques SAS
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 Valeo Systemes Thermiques SAS filed Critical Valeo Systemes Thermiques SAS
Publication of EP2072936A1 publication Critical patent/EP2072936A1/de
Application granted granted Critical
Publication of EP2072936B1 publication Critical patent/EP2072936B1/de
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Images

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
    • F25B40/00—Subcoolers, desuperheaters or superheaters
    • 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
    • F25B2341/00—Details of ejectors not being used as compression device; Details of flow restrictors or expansion valves
    • F25B2341/06—Details of flow restrictors or expansion valves
    • F25B2341/068—Expansion valves combined with a sensor
    • F25B2341/0683—Expansion valves combined with a sensor the sensor is disposed in the suction line and influenced by the temperature or the pressure of the suction gas
    • 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
    • F25B2500/18—Optimization, e.g. high integration of refrigeration components

Definitions

  • the invention relates to air conditioning circuits operating with a refrigerant fluid, in particular for motor vehicles. More particularly, the invention relates to a heat exchange device for such a circuit.
  • Air conditioning circuits operating with a refrigerant fluid are known.
  • Such a circuit typically comprises, in the direction of circulation of the refrigerant fluid, a compressor, a condenser, an expansion device and an evaporator.
  • An internal heat exchanger is a device allowing the refrigerant fluid to exchange heat with the same fluid, but in a different temperature and pressure state.
  • the high pressure refrigerant fluid from the compressor is condensed in the condenser and then passes into a first portion of the internal exchanger. Then, the coolant is expanded by the expansion device. The low-pressure refrigerant leaving the expander then passes through the evaporator for evaporation and into a second portion of the internal heat exchanger before returning to the compressor.
  • the hot fluid at high pressure exchanges heat with the cold fluid at low pressure.
  • the internal exchanger ensures a heat exchange of the refrigerant at two different points of the air conditioning circuit.
  • the evaporator makes it possible to produce a cold air flow, or air-conditioned, that can be sent, for example, into the passenger compartment of a motor vehicle.
  • An air conditioning circuit thus comprises a large number of active elements, that is to say, capable of modifying the pressure and temperature conditions of the refrigerant, as well as a large number of interconnecting connecting pieces. of fluid the different active elements between them.
  • An air conditioning circuit is generally bulky and expensive manufacturing.
  • an air conditioning circuit With a small footprint, an air conditioning circuit must be more and more efficient and durable, that is to say without leakage of the refrigerant.
  • the document FR 2858397 is an example of this integration.
  • the document JP2001021234 presents an example comprising an internal heat exchanger, an evaporator and an expansion device
  • the object of the invention is to overcome the aforementioned drawbacks.
  • the invention proposes a heat exchange module for an air conditioning circuit operating with a refrigerant, comprising an evaporator, an internal heat exchanger and a receiving housing for an expansion device.
  • the evaporator, the internal heat exchanger and the housing form a unitary assembly and in that the housing is located integrally inside the internal heat exchanger.
  • the overall size of the evaporator, the internal heat exchanger and the expansion device is considerably reduced, the connecting pieces between these elements being particularly small or non-existent.
  • the resulting assembly is thus easier to integrate, for example in a motor vehicle.
  • the risk of leakage is limited by the reduction in the number of components. It is the same cost of manufacturing such a set.
  • the expansion device inside the internal heat exchanger makes it possible to use an internal heat exchanger having dimensions similar to those of the evaporator. In doing so, the exchange surface between the high pressure fluid and the low pressure fluid passing through the internal heat exchanger is greater, making this internal heat exchanger more efficient.
  • unitary means that the evaporator, the internal heat exchanger and the housing are indissociable.
  • the internal heat exchanger comprises a plurality of contiguous plates each provided with at least one hole, the plurality of holes forming the housing for the expansion device.
  • a first end of the housing is formed by the inlet port of the evaporator.
  • the first end of the housing comprises means for positioning the expansion device.
  • the housing is traversed by the refrigerant fluid.
  • the housing in which is disposed the expansion device is a channel in which the fluid flows.
  • a securing means permanently holds the expansion device inside the internal heat exchanger.
  • the internal heat exchanger comprises a first and a second section, the first section being separated from the second section by a separating plate.
  • the housing is accessible through the outlet of the heat exchange module.
  • the receiving housing is a portion of a conduit extending within the first and second sections.
  • the invention also relates to a heat exchange device in which the expansion device is housed in the housing.
  • a heat exchange device has the advantage of combining three components of an air conditioning system according to a single unit. In this way, an air-conditioning system equipped with this unitary unit has an extremely small footprint, a greatly reduced manufacturing cost (all connections connecting the evaporator, the internal heat exchanger and the expansion device are removed) and a improved sealing (the connectors do not exist any more).
  • a first channel and a second channel separate from each other are formed by the expansion device and the conduit.
  • the first channel extends within the first section and the second channel extends within the second section.
  • the first channel is aligned with the second channel.
  • the expansion device comprises a head cooperating with the separating plate to form the first and second channels.
  • the expansion device is a tube orifice.
  • the expansion device is a thermostatic expansion valve.
  • a step c) follows step b) and comprises fixing the expansion device inside the internal heat exchange module.
  • the air conditioning circuit 1 known to the figure 1 comprises a compressor 2, a condenser 3, an internal heat exchanger 4, an expansion device 5 and an evaporator 6, these different elements being connected to each other by connecting pieces, such as tubes, tubes, pipes or the like, so as to ensure a flow of refrigerant.
  • the refrigerant fluid is typically a fluid operating in a subcritical regime, such as the fluid R134a or the fluid R152a.
  • the refrigerant, sent by the compressor 2, passes through the condenser 3, from which it emerges in a state of high pressure and high temperature.
  • the refrigerant then passes through the internal heat exchanger 4, then is expanded in the expansion device 5.
  • the fluid thus expanded is then conveyed to the evaporator 6, before joining the internal heat exchanger 4 in a state of low pressure and low temperature, that it crosses.
  • the low-pressure refrigerant from the evaporator 6 exchanges heat with the same high-pressure refrigerant from the condenser 3.
  • the air conditioning circuit 100 comprises the compressor 2, the condenser 3 and a heat exchange module 8, also called combined heat exchange unit.
  • the heat exchange module 8 comprises the evaporator 6 and the internal heat exchanger 4 and a receiving housing 9.
  • the evaporator 6 and the internal heat exchanger 4 are contiguous to one another. to each other via respective contact faces.
  • the receiving housing 9 is housed inside the internal heat exchanger.
  • the evaporator 6, the internal heat exchanger 4 and the receiving housing 9 form a unitary unit.
  • the receiving housing 9 is adapted to accommodate the expansion device 5. In doing so, when the expansion device 5 is housed inside the receiving housing 9, the heat exchange module 8 forms with the expansion device 5 a heat exchange device 10.
  • the evaporator 6 comprises a bundle of tubes 11 aligned for the circulation of the refrigerant.
  • intercalated heat exchange tabs 12 to increase the heat exchange between the refrigerant and an external fluid, for example air, passing through the heat exchange module 8.
  • the spacers 12 are in the form of corrugated metal strips whose apices come into contact with the tubes 11.
  • the tubes 11 are of the so-called "plate” type, that is to say a tube 11 is constituted by the union of two generally flat elements shaped so as to allow the passage of a fluid.
  • a plate tube may be formed using metal plates stamped to provide one or more fluid circulation passages, or stamped plates and a spacer forming said fluid circulation passages.
  • the tubes 11 are received at one of their ends in a manifold, made here in the form of a generally parallelepipedic header box 13.
  • the manifold 13 is partitioned to provide a first box portion 14 having an inlet or a coolant inlet 15 and a second box portion 16 having a coolant outlet or outlet 17.
  • the tubes 11 are arranged here so as to ensure a circulation of the coolant in a "U", the end of each of the branches of this U opening respectively in the first 14 and second 16 parts of boxes.
  • the refrigerant entering through the inlet port 15 in the liquid portion 14 flows through the tubes 11 in a first, a second pass and a third pass by exchanging heat with the external fluid. This causes evaporation of the coolant, which exits the box portion 16 through the outlet orifice 17.
  • the tube 11 located at the end of the beam closest to the coolant outlet is in contact with the internal heat exchanger 4.
  • the evaporator 6 here has a contact face 18 with the exchanger 4 substantially flat.
  • the internal heat exchanger 4 is here of the so-called "stacked plate” type, that is to say essentially constituted by the stack of plates shaped so as to have fluid circulation channels 20 and conduits 21 of fluid circulation.
  • the internal heat exchanger 4 essentially consists of the successive and repeated stacking of a high pressure plate 22, a low pressure plate 23 and again a high pressure plate 22, and so on .
  • the high pressure plate 22 is shown in figure 3a and is in the form of a rectangular metal plate in which is formed a recess 24 for forming a reservoir.
  • the recess 24 covers a large part of the surface of the plate.
  • the hollow 24 may be made by stamping the high pressure plate 22.
  • the high pressure plate 22 further has a first hole 25 and a second hole 26 for passing coolant fluid at low pressure.
  • the holes 25 and 26 here have a circular contour and are each arranged in a corner of the high pressure plate 22, the two corners being arranged in the same first side C1 of the plate with respect to a longitudinal axis A of the plate of 22.
  • the holes 25 and 26 are left free by the recess 24, that is to say that they do not cooperate with the recess 24 for the circulation of the refrigerant, as described later.
  • the high pressure plate 22 also includes a third hole 27 and a fourth hole 28 for passing high pressure refrigerant.
  • the holes 27 and 28 have a circular contour and are each arranged in a corner of the high pressure plate 22, the two corners being arranged in the same second side C2 of the plate relative to a longitudinal axis A of the high plate. pressure 22.
  • the holes 27 and 28 are therefore in a different side of the plate than the side comprising the holes 25 and 26.
  • the holes 27 and 28 cooperate with the recess 24 for the circulation of the refrigerant fluid under high pressure, as described later.
  • the low pressure plate 23 is shown in figure 3b and is in the form of a rectangular metal plate in which is formed a recess 29 for forming a reservoir.
  • the low pressure plate 23 is of identical dimensions to those of the high pressure plate 22.
  • the hollow 29 covers a wide part of the surface of the plate.
  • the hollow 29 can be made by stamping the low-pressure plate 23.
  • the low pressure plate 23 further has a first hole 30 and a second hole 31 for passing coolant fluid at low pressure.
  • the holes 30 and 31 here have a circular contour and are each arranged in a corner of the low pressure plate 23, the two corners being arranged in the same first side C1 of the plate with respect to a longitudinal axis A of the plate of Low pressure 23.
  • the holes 30 and 31 cooperate with the recess 29 for the circulation of the refrigerant, as described later.
  • the low pressure plate 23 also includes a third hole 32 and a fourth hole 33 for passing high pressure refrigerant.
  • the holes 32 and 33 have a circular contour and are each arranged in a corner of the low pressure plate 23, the two corners being arranged in the same second side C2 of the plate with respect to a longitudinal axis A of the bottom plate. 23.
  • the holes 32 and 33 are located in a different side of the plate than the side comprising the holes 30 and 31.
  • the holes 32 and 33 are left free by the recess 29, that is to say that they do not cooperate with the hollow 29 for the circulation of the refrigerant.
  • the surface of the low pressure plate 23 covers, and thus close, the hollow 24 of the high pressure plate 22 so as to form a reservoir adapted to receive refrigerant fluid at high pressure.
  • the hollow of the high pressure plate with the low pressure plate delimits a space constituting a refrigerant flow circuit.
  • the surface of the high pressure plate 22 covers the hollow 29 of the low pressure plate 23 so as to form a reservoir adapted to receive refrigerant fluid at low pressure.
  • the first hole 30 of the low pressure plate 23 is arranged in such a way that, when the low pressure plate 23 is stacked on the high pressure plate, the first hole 30 of the low pressure plate 23 coincides with the first hole 25 of the high pressure plate 22.
  • the second hole 31 coincides with the second hole 26
  • the third hole 32 coincides with the third hole 27
  • the fourth hole 33 coincides with the fourth hole 28.
  • the set of first holes 25, 30 form a first duct 34
  • the set of second holes 26, 31 form a second duct 35
  • the set of third holes 27, 32 form a third duct 36
  • all fourth holes 28, 33 form a fourth duct 37.
  • the internal heat exchanger 4 makes it possible to ensure a heat exchange between the high-pressure refrigerant circulating in the tanks 24 and the refrigerant fluid at low pressure in the tanks 29.
  • the stack ends on one side with a first end plate 38 which is in the form of a rectangular metal plate of dimensions identical to those of the high pressure plates 22 or low pressure plates 23.
  • the first plate end 38 comprises a recess 39 covered by a low pressure plate 23 and a first hole 40 coinciding with the first hole 30 of the low pressure plate 23 and a second hole 41 coinciding with the second hole 31 of the low-pressure plate 23.
  • the first hole 40 does not cooperate with the recess 39. Since this first end plate 38 comprises only two holes 40 and 41, it closes the second duct 35 and the fourth duct 37.
  • the stack ends with a second end plate 42 having holes coinciding with the holes 26 and 28 of a high pressure plate 22. These holes constitute the inlet 43 and the outlet 44 of the heat exchange module 8.
  • the second end plate 42 closes the first duct 34 and the third duct 36.
  • Another hole 47 coinciding with the holes 27, 32 of the high pressure plates 22 and low pressure 23, is formed on the second end plate 42. This hole 47 is aligned with the holes 27, 32 and forms an opening of the third duct 36 towards the outside of the heat exchange module 8. The utility of this hole 47 will be described later.
  • the path of the refrigerant in the internal heat exchanger 4 is as follows.
  • the high-pressure refrigerant enters the interior of the internal heat exchanger 4 through the inlet 43. While traveling through the fourth duct 37 until reaching the first end plate 38, the refrigerant passes through each reservoir 24 to arrive in the third conduit 36. The latter 36 leads to the inlet 15 of the evaporator 6.
  • each reservoir 29 allows the cooling fluid to be conveyed to the second duct 35 to exit the internal heat exchanger 4 via the outlet 44.
  • the refrigerant fluid penetrating inside the evaporator 6 at its inlet 15 must be at low pressure.
  • the third conduit 36 carries refrigerant fluid at high pressure.
  • an expansion device 5 is located in a receiving housing 9.
  • This receiving housing 9 is formed by the third conduit 36.
  • the housing does not constitute an additional space allocated to the expansion device 5 which would increase the dimensions of the heat exchange module 8.
  • the receiving housing 9 is therefore formed by all the holes 27, 32 of the plates. 22, 23 of the internal heat exchanger 4 and the hole 47 of the second end plate 42.
  • This housing is fully located in the internal heat exchanger 4.
  • the overall size of the heat exchange module 8 is dictated by the dimensions of the evaporator 6, the fact that the expansion device can be housed at the inside of the internal heat exchanger 4 makes it possible to size the latter 4 according to the same dimensions as those of the evaporator 6.
  • the housing were located outside the internal heat exchanger 4, the plates 22 and 23 constituting it should be of reduced dimensions so that the overall size of the housing and of the internal heat exchanger is not greater than that of the evaporator 6. Consequently, using the third duct 36 as receiving housing, the internal heat exchanger 4 offers larger exchange surfaces between the low pressure refrigerant and the high pressure refrigerant, thus improving the efficiency of the internal heat exchanger 4.
  • the integration of the expansion device 5 inside the receiving housing 9 of the heat exchange module 8 in order to form the heat exchange device 10 is via the hole 47 of the second heat sink plate. end 42. Indeed, when the plates are contiguous to each other, the hole 47 of the second end plate 42 gives access to the receiving housing 9. thus, once the heat exchange module 8 is formed, the expansion device 5 is introduced inside the receiving housing 9 via the hole 47 of the second end plate 42.
  • the housing 9 is thus defined by an alignment of holes 27, 32, 47.
  • This housing 9 is delimited by the inlet orifice 15 of the evaporator 6 and by the second end plate 42.
  • the orifice of In this connection when the expansion device 5 is inside the heat exchange module 8, it must not move inside the housing.
  • the fastening means 45 comprises a screw thread capable of cooperating with an internal thread arranged on the expansion device 5.
  • the attachment means 45 comprises an internal thread capable of cooperating with a thread arranged on the expansion device 5.
  • the fixing means 45 is in the form of a flexible tab provided with a lug cooperating with a notch.
  • the expansion device 5 is a tube orifice 5a.
  • the term "tube orifice” means a device comprising a tube of internal diameter calibrated so that the high pressure fluid entering the tube relaxes at the outlet of this tube.
  • An exemplary embodiment is shown in figure 3c .
  • the expansion device 5 comprises a body 60 provided with a head 61 and a shank 62.
  • the body 60 is hollow and forms a chamber 68 into which the high-pressure fluid rushes.
  • a positioning means 48 is formed by a flange 70 disposed on the head 61 and a bead 71 formed on the second end plate 42.
  • An identical bead is disposed on the inlet orifice 15 of the evaporator 6 to cooperate with the tail of the expansion device 5 and thus form another positioning means 48.
  • These two positioning means 48 ensure the introduction of the expansion device 5 in the heat exchange module 8 to a desired position.
  • the positioning means are associated with O-rings 46 to ensure a seal between the receiving housing 9 and the expansion device 5.
  • the shank 62 comprises the threading cooperating with the tapping to form the fastening means 45 of the expansion device 5.
  • the threading is situated on the head 61.
  • the head 61 of the expansion device 5 is shaped to form a plug hole 47 of the second end plate 42.
  • the head 61 completely closes the hole 47.
  • the heat exchange device 10 thus formed is completely ready for use.
  • the existence of the hole 47 of the second end plate 42 simplifies the manufacturing process of the heat exchange device 11. In fact, it suffices to form the heat exchange module 8 by brazing all the plates forming the internal heat exchanger 4 on the evaporator 6 and then insert the expansion device 5 in the receiving housing 9. No additional step is necessary since the expansion device 5 closes itself completely the hole 47 by which it was introduced into the heat exchange module 8.
  • the expansion device 5 being according to this embodiment a tube orifice 5a, its tail 62 comprises a tube 72 ensuring the relaxation of the high pressure fluid.
  • the tube is in fluid communication on one side with the chamber 68 supplying the tube 72 with high pressure fluid and on the other side with the inlet port 15 for delivering to the interior of the evaporator 6 of the fluid at low pressure.
  • the figure 4 illustrates a second embodiment of a heat exchange module 8 '.
  • the figure 6 illustrates the internal heat exchanger 4 'according to this second embodiment.
  • the heat exchange module 8 ' according to the second embodiment comprises the evaporator 6 and a heat exchanger 4'.
  • thermostatic expansion valve means a device comprising a body provided with a chamber in which the fluid arrives at high pressure and a needle varying the passage section of the outlet of the chamber, the needle being provided with a spring and a bulb in contact with the low pressure fluid.
  • the internal heat exchanger 4 comprises a first 50 and a second section 51.
  • the first section 50 corresponds to the internal heat exchanger 4 according to the first embodiment with the exception that the second end plate 42 is replaced by a separating plate 52.
  • This separating plate 52 is in the form of shape of a rectangular metal plate of dimensions identical to those of the high pressure plates 22 or low pressure 23.
  • the partition plate 52 comprises three holes 53 arranged in such a way that the second 35, third 36 and fourth 37 ducts are open towards the second section 51.
  • the second section 51 comprises a stack of high pressure plates 22 'and low pressure 23'.
  • a terminating plate 53 and the separating plate 52 delimits the second section 51.
  • the high pressure plate 22 'of the second section 51 differs from the high pressure plate 22 of the first section 50 only from the point of view of cooperation.
  • holes with the hollow 24 ' So as illustrated in figure 4a , the high pressure plate 22 'comprises four holes 25', 26 ', 27' and 28 'arranged identically to the holes 25, 26, 27 and 28.
  • the holes cooperating with the hollow 24 'of the high pressure plate 22' are the holes 26 'and 27'. These are the centrally opposed holes relative to each other with respect to the center O of the plate 22 '.
  • the low pressure plate 23 'of the second section 51 it is the holes 30' and 33 'which cooperate with the hollow 29'. These holes are opposite one another with respect to the center O of the low pressure plate 23 '.
  • the latter 4' comprises five ducts.
  • the second 35, the third 36 and the fourth 37 ducts each run entirely through the first 50 and the second section 51.
  • the first duct 34 is closed off by the separation plate 52.
  • a fifth duct 54 is formed by the alignment of the holes 25. and 30 'between the separating plate 52 and the end plate 53.
  • the receiving housing 9 is formed by the portion of the third conduit 36 belonging to the first section 50.
  • the expansion device 5 is a thermostatic expansion valve 5b comprises a body 60 provided with a head 61 and a shank 62.
  • the head 61 of the body 60 comprises a bulb 63 and a spring 64.
  • This bulb 63 and this spring 64 are attached to one end of a needle 65.
  • the tail 62 comprises a fluid outlet 66 whose section is variable according to the position of the other end of the needle 65.
  • the position of the needle 65 is controlled by the bulb 63 which responds to the pressure and temperature differences of the low pressure fluid with which it is in contact.
  • the thermostatic expansion valve 5b makes it possible to control overheating.
  • the high-pressure fluid enters the body 60 via a window 67 giving access to a chamber 68 connected to the fluid outlet 66.
  • the shank 62 When the expansion device 5 is housed inside the receiving housing 9, the shank 62, comprising a thread or a tapping, cooperates with the attachment means 45 of the inlet orifice 15 to hold the thermostatic expansion valve in position. position.
  • An O-ring 46 provides sealing.
  • the head 61 it cooperates with the separating plate 52 to completely close the third duct 36.
  • the third duct 36 splits into a first channel 69 extending inside the first section 50 and a second channel 70 extending inside the second section 51.
  • the first channel 69 and the second channel 70 thus formed are distinct and are not fluidly connected to each other.
  • the path of the refrigerant in the internal heat exchanger 4 ' is as follows.
  • the high-pressure refrigerant fluid enters the interior heat exchanger 4 'through the inlet 43 and travels through the fifth duct 54.
  • the refrigerant high pressure runs along the fourth duct 37 and passes from the first section 50 to the second section 51 through the partition wall 52. Then it reaches the first channel 69 through the tanks 24 and penetrates inside of the chamber 68 of the thermostatic expansion valve 5b via the window 67. If the needle 65 does not completely close the outlet 66, the high pressure refrigerant is expanded through this outlet 66 to reach the evaporator 6 at its level. inlet port 15.
  • the low-pressure refrigerant fluid enters the internal heat exchanger 4 'via the outlet port 17. It traverses the first conduit 34 until it reaches the plate 52 and arrives at the second duct 36 via the tanks 24. Traveling in the second duct 36, the low-pressure refrigerant crosses the separation plate and reaches the second section 51. It arrives at the second duct 36. inside the second channel 70 and out of the internal heat exchanger 4 'via the outlet 44.
  • the low-pressure refrigerant fluid When the low-pressure refrigerant fluid enters the second channel 70, it is in contact with the head 61, and more precisely with the bulb 63 of the thermostatic expansion valve 5b.
  • the position of the needle 65 varies, this regulating the expansion of the high pressure refrigerant fluid through the tail 62 of the thermostatic expansion valve 5b.
  • the particular arrangement of the ducts and channels in the first 50 and the second section 51 provides a channel (first channel 69) carrying high pressure refrigerant fluid aligned with a channel (second channel 70) conveying fluid low pressure refrigerant.
  • a thermostatic expansion valve 5b requiring to be in contact with both the high pressure refrigerant fluid and the low pressure refrigerant fluid, the arrangement of the conduits can cause a loss of compactness of the heat exchange device.
  • the combination of the plates of the first section, the separating plate and the plates of the second section implies an arrangement of the ducts which ensures the use of a thermostatic expansion valve 5b in the exchange device of the second section.
  • Another advantage due to the particular arrangement of the heat exchange module 8 comprising the internal heat exchanger 4 ' is the fact of being able to manufacture it completely and then to insert the expansion device 5 via the outlet 44 and fix it. In this respect, the manufacture of the heat exchange device 10 is facilitated since the opening through which the expansion device 5 is inserted is the output 44 of the module connected to the compressor 2.
  • the thermostatic expansion valve 5b is replaced by the tube orifice 5a of the first embodiment. Since the tube orifice is less expensive than a thermostatic expansion valve but offers lower performance than the thermostatic expansion valve, it is advantageous to be able to use two types of expansion device with the same structure of the heat exchange module comprising two sections. Thus, according to the demands of the car manufacturers, only the type of expansion device used changes, this implying a standardization of the heat exchange module used and a reduction in costs.
  • the method of manufacturing the heat exchange device 10 is as follows. First, the already formed evaporator is attached to the plates forming the internal heat exchanger, themselves contiguous to each other. The evaporator and the plates are then brazed in an oven to form the heat exchange module 8. By the action of brazing, the heat exchange module is unitary, that is to say inseparable. It is understood from the foregoing that the stack of the plates forms both the internal heat exchanger and the receiving housing 9. Next, an expansion device 5 is introduced inside the receiving housing 9 and fixed to the heat exchange module 8. The heat exchange device 10 is then formed.
  • the high-pressure plates 22 and the low-pressure plates 23 comprise turbulence means 80. These turbulence means improve the heat exchange between the high-pressure fluid and the low-pressure fluid inside the heat exchanger. internally by creating turbulence in the refrigerant flow. These turbulence means comprise for example ribs or pads formed in the recess 24, 29.
  • Embossings 81 are located at the periphery of the holes not cooperating with the hollow of a plate.
  • the holes 25 and 26 are each surrounded by a rib which ensures a seal of these holes vis-à-vis the hollow 24.
  • the fixing means 45 and the positioning means 48 disposed on the inlet orifice 15 of the evaporator may be arranged on the first end plate 38, on the second plate of the end 42, on the separator plate 52 or on the first end plate 38 with at least one high pressure plate and a low pressure plate.
  • the expansion device is partly housed inside the evaporator 6.
  • the fixing means 45 and the positioning means 48 are located on the body 60 of the device 5.
  • the term "partly housed” means that the tail 62 of the expansion device is located inside the evaporator 6.
  • Each plate is rectangular and of center O. All the plates forming the internal heat exchanger 4 are of identical size. In addition, all the plates 19 have the same dimension as the contact face 18 of the evaporator 6. According to an alternative embodiment, the holes of a plate have a square or rectangular contour.
  • low pressure plate is meant a plate ensuring the flow of fluid from one end to another of the plate, the fluid being at low pressure.
  • high pressure plate means a plate ensuring the flow of fluid from one end to another of the plate, the fluid being at high pressure.
  • all the plates from this exchanger must withstand the high pressure values of the fluid.
  • a low pressure plate ensuring the circulation of fluid at low pressure must withstand the high pressure of the fluid since it covers a high pressure plate.
  • the tubes 11 of the evaporator can be formed by extrusion.
  • the evaporator 6 can be of any type.
  • the evaporator 6 has two manifolds 13 located opposite to each other and located at the ends of the evaporator.
  • the structure of the plates forming the internal heat exchanger is adapted.
  • the manifold or boxes of the evaporator 6 are formed by the stack of extruded or stamped plates.
  • the evaporator is 4 or 8 passes.

Landscapes

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

Claims (17)

  1. Wärmeaustauschmodul (8) für einen Klimakreislauf, der mit einem Kühlfluid funktioniert, umfassend einen Verdampfer (6), einen internen Wärmetauscher (4, 4') und ein Aufnahmegehäuse (9) für eine Entspannungsvorrichtung (5), wobei der Verdampfer (6), der interne Wärmetauscher (4, 4') und das Aufnahmegehäuse (9) eine einheitliche Anordnung bilden, dadurch gekennzeichnet, dass das Aufnahmegehäuse (9) vollständig im Inneren des internen Wärmetauschers (4, 4') angeordnet ist, wobei der interne Wärmetauscher (4, 4') mehrere aneinandergefügte Platten (22, 23, 38, 42, 52, 53) aufweist, die jeweils mit mindestens einem Loch (27, 32, 47) versehen sind, wobei die mehreren Löcher (27, 32, 47) das Aufnahmegehäuse (9) für die Entspannungsvorrichtung (5) bilden.
  2. Wärmeaustauschmodul (8) nach Anspruch 1, wobei ein erstes Ende des Aufnahmegehäuses (9) durch die Eintrittsöffnung (15) des Verdampfers (6) gebildet ist.
  3. Wärmeaustauschmodul (8) nach einem der Ansprüche 1 bis 2, wobei das erste Ende des Gehäuses ein Mittel zum Positionieren (48) der Entspannungsvorrichtung (5) aufweist.
  4. Wärmeaustauschmodul (8) nach einem der Ansprüche 1 bis 3, wobei das Aufnahmegehäuse (9) von dem Kühlfluid durchströmt wird.
  5. Wärmeaustauschmodul (8) nach einem der Ansprüche 1 bis 4, wobei ein Befestigungsmittel (45) die Entspannungsvorrichtung (5) im Inneren des internen Wärmetauschers (4, 4') auf Dauer hält.
  6. Wärmeaustauschmodul nach einem der Ansprüche 1 bis 5, wobei der interne Wärmetauscher (4') einen ersten (50) und einen zweiten (51) Abschnitt aufweist, wobei der erste Abschnitt (50) von dem zweiten Abschnitt (51) durch eine Trennplatte (52) getrennt ist.
  7. Wärmeaustauschmodul (8) nach Anspruch 6, wobei das Aufnahmegehäuse (9) durch den Ausgang (44) des Wärmeaustauschmoduls (8) zugänglich ist.
  8. Wärmeaustauschmodul (8) nach einem der Ansprüche 6 bis 7, wobei das Aufnahmegehäuse (9) ein Teilabschnitt einer Leitung (36) ist, die sich im Inneren des ersten (50) und des zweiten (51) Abschnitts erstreckt.
  9. Wärmetauschvorrichtung (10) nach einem der Ansprüche 1 bis 8, wobei die Entspannungsvorrichtung (5) im Aufnahmegehäuse (9) angeordnet ist.
  10. Wärmetauschvorrichtung (10) nach den Ansprüchen 8 und 9, wobei ein erster Kanal (69) und ein zweiter Kanal (70), die voneinander verschieden sind, durch die Entspannungsvorrichtung (5) und die Leitung (36) gebildet sind.
  11. Wärmetauschvorrichtung (10) nach Anspruch 10, wobei sich der erste Kanal (69) im Inneren des ersten Abschnitts (50) erstreckt und sich der zweite Kanal (70) im Inneren des zweiten Abschnitts (51) erstreckt.
  12. Wärmetauschvorrichtung (10) nach Anspruch 11, wobei der erste Kanal (69) mit dem zweiten Kanal (70) ausgerichtet ist.
  13. Wärmetauschvorrichtung nach einem der Ansprüche 10 bis 12, wobei die Entspannungsvorrichtung (5) einen Kopf aufweist, der mit der Trennplatte (52) zusammenwirkt, um den ersten (69) und den zweiten (70) Kanal zu bilden.
  14. Wärmetauschvorrichtung (10) nach einem der Ansprüche 9 bis 13, wobei die Entspannungsvorrichtung (5) eine Rohröffnung (5a) ist.
  15. Wärmetauschvorrichtung (10) nach einem der Ansprüche 9 bis 13, wobei die Entspannungsvorrichtung (5) ein thermostatisches Expansionsventil (5b) ist.
  16. Verfahren zur Herstellung einer Wärmetauschvorrichtung nach einem der Ansprüche 10 bis 15, das die folgenden aufeinanderfolgenden Schritte aufweist:
    a) Bilden eines Moduls (8) nach den Ansprüchen 7 bis 9, das den Verdampfer (6) und den internen Wärmetauscher (4, 4') aufweist, durch Löten,
    b) Einführen der Entspannungsvorrichtung (5) ins Innere des internen Wärmetauschers (4, 4').
  17. Verfahren zur Herstellung einer Wärmetauschvorrichtung nach Anspruch 16, wobei auf den Schritt b) ein Schritt c) folgt und das Befestigen der Entspannungsvorrichtung (5) im Inneren des internen Wärmetauschers (4, 4') aufweist.
EP08171881.9A 2007-12-20 2008-12-17 Einheitlicher Wärmetauscher für Klimakreislauf Active EP2072936B1 (de)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
FR0708967A FR2925664B1 (fr) 2007-12-20 2007-12-20 Echangeur de chaleur unitaire pour un circuit de climatisation

Publications (2)

Publication Number Publication Date
EP2072936A1 EP2072936A1 (de) 2009-06-24
EP2072936B1 true EP2072936B1 (de) 2019-07-03

Family

ID=39744836

Family Applications (1)

Application Number Title Priority Date Filing Date
EP08171881.9A Active EP2072936B1 (de) 2007-12-20 2008-12-17 Einheitlicher Wärmetauscher für Klimakreislauf

Country Status (2)

Country Link
EP (1) EP2072936B1 (de)
FR (1) FR2925664B1 (de)

Family Cites Families (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0814702A (ja) * 1994-06-27 1996-01-19 Nippondenso Co Ltd 積層型蒸発器
JP3596047B2 (ja) * 1994-10-21 2004-12-02 株式会社デンソー 積層型熱交換器
JP3674060B2 (ja) * 1994-10-25 2005-07-20 株式会社デンソー 積層型熱交換器の製造方法
JPH08136086A (ja) * 1994-11-01 1996-05-31 Nippondenso Co Ltd 冷媒蒸発器
JPH0949671A (ja) * 1995-05-29 1997-02-18 Hitachi Ltd 冷凍空調装置
JPH10103812A (ja) * 1996-09-27 1998-04-24 Calsonic Corp 補助熱交換器及び膨張弁を付属させたエバポレータ
DE19805285A1 (de) * 1998-02-10 1999-08-12 Behr Gmbh & Co Verdampfereinheit für eine Klimaanlage
JPH11310032A (ja) * 1998-04-27 1999-11-09 Calsonic Corp 自動車用空気調和装置
JP2001021234A (ja) * 1999-07-05 2001-01-26 Zexel Valeo Climate Control Corp 冷房装置
JP4083032B2 (ja) * 2003-02-13 2008-04-30 株式会社テージーケー エバポレータ
FR2858397B1 (fr) 2003-07-29 2005-12-23 Valeo Climatisation Dispositif pour l'adaptation d'un detendeur a l'evaporateur d'un appareil de climatisation
WO2006065185A1 (en) * 2004-12-16 2006-06-22 Volvo Lastvagnar Ab Arrangement and method relating to cooling systems

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
None *

Also Published As

Publication number Publication date
FR2925664A1 (fr) 2009-06-26
FR2925664B1 (fr) 2018-04-27
EP2072936A1 (de) 2009-06-24

Similar Documents

Publication Publication Date Title
EP0774102B1 (de) Verflüssiger mit einbezogenem behälter für klimaanlage eines kraftfahrzeuges
EP1992891B1 (de) Kühler, insbesondere für einen Klimaanlagenschaltkreis eines Kraftfahrzeugs, und einen solchen Kühler umfassender Schaltkreis
EP2118608B1 (de) Wärmetauscher und solch einen tauscher enthaltende eingebaute anordnung
FR2947041A1 (fr) Condenseur avec reserve de fluide frigorigene pour circuit de climatisation
EP2402694B1 (de) Kondensator insbesondere für ein klimaanlagensystem eines kraftfahrzeugs, und mit einem solchen kondensator ausgestatteter wärmetauscher
EP2726808A1 (de) Wärmetauscher, gehäuse und klimaanlagenkreis mit einem solchen wärmetauscher
EP2064506A1 (de) Wärmetauscher, insbesondere ein systemluftkühler
FR2973106A1 (fr) Renfort de liaison entre plaques d'un echangeur de chaleur
FR2916835A1 (fr) Module d'echange de chaleur pour un circuit de climatisation
FR2846736A1 (fr) Module d'echange de chaleur a plaques empilees, notamment pour un vehicule automobile
EP2912396A2 (de) Wärmetauscher, insbesondere für ein kraftfahrzeug
WO2003056268A1 (fr) Elément de circuit pour échangeur de chaleur, notamment de véhicule automobile et échangeur de chaleur ainsi obtenu
FR2748316A1 (fr) Echangeur de chaleur a boite collectrice tubulaire et patte de fixation
FR2898405A1 (fr) Echangeur de chaleur, en particulier refroidisseur de gaz, comportant deux nappes de tubes reliees
EP1817536A1 (de) Wärmetauscher mit mindestens einem flansch für den verteiler des wärmetauschers und behälter dafür
FR2936043A1 (fr) Echangeur de chaleur a tubes
EP2072936B1 (de) Einheitlicher Wärmetauscher für Klimakreislauf
WO2016097134A1 (fr) Boite collectrice pour echangeur de chaleur et echangeur de chaleur equipe de ladite boite collectrice
EP2633255B1 (de) Wärmetauscher mit seitlicher flüssigkeitszufuhr
EP1676088B1 (de) Strömungselement für einen wärmetauscher und so erhaltener wärmetauscher
FR2992713A1 (fr) Faisceau d'echange de chaleur et echangeur de chaleur comprenant ledit faisceau
EP2372288B1 (de) Wärmetauscher für Klimaanlage mit reduzierten Enden
FR3060724A1 (fr) Echangeur thermique, notamment evaporateur, muni d'un dispositif de raccordement pour l'introduction et l'extraction d'un fluide caloporteur.
FR2906353A1 (fr) Echangeur de chaleur interne pour circuit de fluide refrigerant
FR2755220A1 (fr) Boite collectrice a reservoir integre pour echangeur de chaleur, notamment de vehicule automobile

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

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

17P Request for examination filed

Effective date: 20091209

17Q First examination report despatched

Effective date: 20100122

AKX Designation fees paid

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

RAP3 Party data changed (applicant data changed or rights of an application transferred)

Owner name: VALEO SYSTEMES THERMIQUES

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: 20170314

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 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: GB

Ref legal event code: FG4D

Free format text: NOT ENGLISH

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: 1151512

Country of ref document: AT

Kind code of ref document: T

Effective date: 20190715

REG Reference to a national code

Ref country code: IE

Ref legal event code: FG4D

Free format text: LANGUAGE OF EP DOCUMENT: FRENCH

REG Reference to a national code

Ref country code: DE

Ref legal event code: R096

Ref document number: 602008060569

Country of ref document: DE

REG Reference to a national code

Ref country code: NL

Ref legal event code: MP

Effective date: 20190703

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: 1151512

Country of ref document: AT

Kind code of ref document: T

Effective date: 20190703

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

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: 20191003

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: 20191003

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: 20190703

Ref country code: NL

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: 20190703

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: 20191104

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: 20190703

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: 20190703

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: 20190703

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: 20190703

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: 20190703

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 FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20190703

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: 20190703

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: 20191004

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: 20191103

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: 20190703

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

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: 20190703

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: 20190703

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: 20190703

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: 20190703

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: 20190703

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

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: 20200224

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: 20190703

REG Reference to a national code

Ref country code: DE

Ref legal event code: R097

Ref document number: 602008060569

Country of ref document: DE

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

PG2D Information on lapse in contracting state deleted

Ref country code: IS

REG Reference to a national code

Ref country code: CH

Ref legal event code: PL

26N No opposition filed

Effective date: 20200603

REG Reference to a national code

Ref country code: BE

Ref legal event code: MM

Effective date: 20191231

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: 20190703

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: 20190703

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

Effective date: 20191217

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: 20191217

Ref country code: LU

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

Effective date: 20191217

Ref country code: IE

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

Effective date: 20191217

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: 20191231

Ref country code: LI

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

Effective date: 20191231

Ref country code: CH

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

Effective date: 20191231

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: 20190703

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: 20081217

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: 20190703

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

Ref country code: FR

Payment date: 20221220

Year of fee payment: 15

Ref country code: DE

Payment date: 20221209

Year of fee payment: 15

P01 Opt-out of the competence of the unified patent court (upc) registered

Effective date: 20230528