Classifications

• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
  • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
  • F16K3/00—Gate valves or sliding valves, i.e. cut-off apparatus with closing members having a sliding movement along the seat for opening and closing
  • F16K3/22—Gate valves or sliding valves, i.e. cut-off apparatus with closing members having a sliding movement along the seat for opening and closing with sealing faces shaped as surfaces of solids of revolution
  • F16K3/24—Gate valves or sliding valves, i.e. cut-off apparatus with closing members having a sliding movement along the seat for opening and closing with sealing faces shaped as surfaces of solids of revolution with cylindrical valve members
  • F16K3/26—Gate valves or sliding valves, i.e. cut-off apparatus with closing members having a sliding movement along the seat for opening and closing with sealing faces shaped as surfaces of solids of revolution with cylindrical valve members with fluid passages in the valve member
  • F16K3/262—Gate valves or sliding valves, i.e. cut-off apparatus with closing members having a sliding movement along the seat for opening and closing with sealing faces shaped as surfaces of solids of revolution with cylindrical valve members with fluid passages in the valve member with a transverse bore in the valve member
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
  • F16H—GEARING
  • F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
  • F16H61/02—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing characterised by the signals used
  • F16H61/0262—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing characterised by the signals used the signals being hydraulic
  • F16H61/0276—Elements specially adapted for hydraulic control units, e.g. valves
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
  • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
  • F16K11/00—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves
  • F16K11/02—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit
  • F16K11/06—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit comprising only sliding valves, i.e. sliding closure elements
  • F16K11/065—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit comprising only sliding valves, i.e. sliding closure elements with linearly sliding closure members
  • F16K11/07—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit comprising only sliding valves, i.e. sliding closure elements with linearly sliding closure members with cylindrical slides
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
  • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
  • F16K11/00—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves
  • F16K11/02—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit
  • F16K11/06—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit comprising only sliding valves, i.e. sliding closure elements
  • F16K11/065—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit comprising only sliding valves, i.e. sliding closure elements with linearly sliding closure members
  • F16K11/07—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit comprising only sliding valves, i.e. sliding closure elements with linearly sliding closure members with cylindrical slides
  • F16K11/0716—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit comprising only sliding valves, i.e. sliding closure elements with linearly sliding closure members with cylindrical slides with fluid passages through the valve member
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
  • F16H—GEARING
  • F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
  • F16H61/02—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing characterised by the signals used
  • F16H61/0262—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing characterised by the signals used the signals being hydraulic
  • F16H61/0276—Elements specially adapted for hydraulic control units, e.g. valves
  • F16H2061/0279—Details of hydraulic valves, e.g. lands, ports, spools or springs

Definitions

• the invention relates to a slide valve, in particular for an automatic transmission for motor vehicles, according to the preamble of claim 1.
• a prior art spool valve includes a spool which is slidable within a spool passage. Furthermore, it is known that
• Connection channels open into a slide channel or are connected to it.
• a slide valve in which a connection bore extends beyond a slide channel.
• a control edge exhibiting a first guide portion is associated with the connection bore and has at least one annular groove in its outer shell surface.
• DE 10 201 1 087 546 A1 relates to a slide valve having a valve slide which can be acted upon by an actuator.
• the valve slide has two axially extending radially encircling and arranged next to control sections recesses.
• Fluid connection between two adjacent connection channels manufactures and the valve slide is guided in the open slide position, a portion of a slide channel between the adjacent connection channels, both the mechanical friction and the Viskosereibung can be reduced. Furthermore can be realized with smaller dimensions and slide valves.
• valve slide in the region of the slide channel between the adjacent connection channels that further guide regions can be omitted.
• a reduction in the diameter of the valve spool and a reduction in the length of the valve spool are possible.
• the slide valve can advantageously be realized without additional sleeve. Also, there are small tolerances with respect to the position of holes. Even undercuts in the housing can be avoided. A reduction of the production steps is possible.
• the guide portion is substantially continuous in a guide outer surface of an adjacent
• Closing section of the valve spool over This advantageously ensures that the guide is essentially not interrupted in the region of control edges or holes. In particular, thereby tilting of the valve spool is prevented and increases the life of the spool valve.
• adjacent cross-sectional recesses are equidistant from each other and / or adjacent guide sections equidistant from each other.
• Another development relates to a point symmetry or axis symmetry in the cross section of the valve spool.
• Connection channels transversely to a longitudinal axis of the slide channel, in particular in a region in which the valve spool is arranged, a larger diameter than a transverse diameter of an adjacent portion of the slide channel.
• connection channel has the advantage that, in particular at low temperatures and thus increased viscosity of the fluid, the connection channel has no significant throttling effect, as a result of which the slide valve can be made smaller.
• valve slide on a passage, which establishes a fluid connection between a working pressure connection channel and a pressure chamber in a pressure build-up position of the valve slide.
• a side facing away from an actuator for the valve spool end face of the valve spool can be acted upon via the pressure chamber with pressure. This can advantageously be generated in the direction of the actuator back pressure and at the same time, the space of the
• Slider valve can be reduced.
• Diameter change is arranged in the longitudinal direction of the valve spool spaced from a control edge of the opening portion. As a result, advantageously, the diameter of the valve spool can be changed without the
• Diameter change takes over the function of a control edge.
• a housing of the spool valve to a passage, which is a fluid connection between a
• Working pressure connection channel and a pressure chamber produces.
• a side facing away from an actuator for the valve spool end face of the valve spool can be acted upon via the pressure chamber with pressure.
• a force counteracting the actuator can advantageously be provided. Due to the fact that the end face is pressed out of the Working pressure port channel can be applied, it is possible to generate a closed loop.
• Figure 1 is a schematic sectional view of a slide valve in one
• Figure 2 is a schematic sectional view of the spool valve of Figure 1 in a closed position
• Figure 3 is a schematic sectional view of the spool valve of Figure 1 in a pressure reduction position
• Figure 4 is a perspective view of a valve spool
• Figure 5 is a schematic cross-sectional view of the spool valve of Figure 1;
• Figure 6 is a schematic sectional view of a second spool valve
• Figure 7 is a schematic cross-sectional view of the second spool valve of Figure 6;
• Figure 8 is a schematic sectional view of a third slide valve
• Figure 9 is a perspective view of a detail of another valve spool.
• Figure 10 is a schematic sectional view of a fourth slide valve.
• FIG. 1 shows a schematic sectional view of a first slide valve 2 in a pressure build-up position.
• the slide valve 2 is provided in particular for an automatic transmission for motor vehicles.
• the slide valve 2 has a housing 4, which is shown hatched in section.
• a Slider channel 6 is formed, which extends at least partially substantially in a cylindrical shape along a longitudinal axis 8.
• a valve slide 10 is slidably disposed, which is shown in a side view in the present case.
• the first slide valve 2 has a tank connection channel 12, a working pressure connection channel 14 and a pressure supply connection channel 16 which each open into the slide channel 6. Via the pressure supply connection channel 16, the slide valve 2 is supplied with a pressurized fluid. By a displacement of the valve spool 10 along the longitudinal axis 8 of the
• Valve spool 10 are brought into the pressure build-up position shown, flows in the fluid from the pressure supply port 16 in the working pressure port 14 according to arrows 18.
• the tank connection channel 12, the working pressure connection channel 14 and the pressure supply connection channel 16 are generally also referred to as a connection channel.
• the valve spool 10 has an opening portion 20 in the longitudinal direction, which is bounded on both sides by a closing portion 22 and a closing portion 24.
• the closing sections 22 and 24 have an outer surface which bears against an inner surface of the slide channel 6 in such a way that the closing sections 22 and 24 respectively close the slide channel 6 in a substantially fluid-tight manner.
• Opening portion 20 of the valve spool 2 has in more detail in Figure 4 and 5 explained cross-sectional recesses 26 and 28 and guide portions 30 and 32.
• the slide channel 6 and the valve slide 10 are thus designed such that the valve slide 10 in the open slide position a fluid connection according to the arrows 18 between the two adjacent connection channels, the working pressure connection channel 14 and the pressure supply connection channel 16, and the valve spool 10 in addition is guided in the open slide position in a region 34 of the slide channel 6 between the adjacent connection channels 14 and 16.
• the cross-sectional recesses 26 and 28 ensure that an opening in the region 34 between the pressure supply connection channel 16 and the
• Working pressure connection channel 14 results.
• the guide portions 30 and 32 are in Region 34 on such inner surfaces of the slide channel 6, that a guide of the valve spool 10 along the longitudinal axis 8 is ensured.
• the tank connection channel 12 opens via a bore 36 in the slide channel 6.
• the bore 36 has in the region of the valve spool substantially a shape of a cylinder, wherein the longitudinal axis of the cylinder substantially with the
• connection channels 14 and 16 are arranged with their respective longitudinal axis 38 and 40 such that the respective longitudinal axis 38, 40 extends substantially transversely to the longitudinal axis 8 of the slide channel 6.
• the bore 36 is associated with the tank connection channel 12 and has a diameter 42.
• the working pressure connection channel 14 has a diameter 44.
• the pressure supply port 16 has a diameter 46.
• the slide channel 6 has a transverse diameter 50.
• the connection channels 12 to 16 thus have a larger transversely to the longitudinal axis 8 of the slide channel 6
• Diameter 42, 44, 46 as the transverse diameter 50 of the slide channel.
• connection channels 14 and 16 have a larger diameter 44 and 46 transversely to the longitudinal axis 8 of the slide channel, which is greater than the transverse diameter 50 in the region of the portion 34 adjacent to the
• Connection channels 14 and 16 is arranged.
• the diameters 44 and 46 can be determined to be about 2.5 mm and the transverse diameter 50 to about 1.5 mm.
• the axially to the longitudinal axis 8 bore 36 may also be formed in the region of the connection channels 14 and 16.
• the connection channel 12 as the connection channels 14 and 16 may be formed transversely to the longitudinal axis 8.
• a force is supplied to the valve spool 10, which starts from an actuator which is arranged opposite to the direction of the arrow 52 in a form not shown.
• the actuator may be, for example, an electromagnet or else a hydraulic drive.
• a pressure chamber 56 which is formed essentially by the end face 54 and the slide channel 6 of the housing 4.
• Two bores 58 and 59 through the housing 4 connect the working pressure port 14 to the pressure chamber 56.
• a regulated pressure in the working pressure port 14 is passed into the pressure chamber 56, whereby this regulated pressure on the end face 54 and in particular can act on the entire cross-sectional area of the slider.
• the regulated pressure thus counteracts the force according to the arrow 52.
• the housing 4 of the spool valve 2 has a passage according to the bores 58 and 59, wherein the passage establishes a fluid connection between the working pressure port 14 and a pressure chamber 56.
• This is a the actuator for the valve spool 10 facing away from end face or end face 54 of the valve spool 10 via the pressure chamber 56 can be acted upon with pressure.
• FIG. 2 shows in a schematic sectional view the first slide valve 2 from FIG. 1 in a closed position.
• the valve spool 10 is located with the closing portion 24 according to a sealing length 62 in the portion 34 of the
• the sealing portion 22 is located according to a sealing length 64 in a portion 66 of the slide channel 6 between the tank connection channel 12 and the working pressure connection channel 14 and thus closes the section 66.
• the slide valve 2 alternatively be configured such that either by the design of the slide channel 6 or the valve spool 10 no two sealing lengths 64 or 62 result and thus always a connection from the connection channel 16 to the connection channel 14 or from the connection channel 14 to the connection channel 12 is present.
• FIG. 3 shows a schematic sectional view of the first slide valve 2 in a pressure reduction position.
• fluid 68 can flow from the working pressure connection channel 14 into the tank connection channel 12 in accordance with arrows 68.
• the pressure reduction position corresponds to the pressure build-up position of an open slide position. In the pressure reduction position shown represents the
• Valve spool 10 a fluid connection between the two adjacent
• Connection channels 12 and 14 forth and the valve spool 10 is guided simultaneously in the portion 66 of the slide channel 6.
• FIG. 4 shows the valve slide 10 from FIGS. 1 to 3 in a schematic perspective view. It is the longitudinal axis 8 of the slide channel. 6
• the closing portions 22 and 24 have respective guide outer surfaces 68 and 70 which are formed substantially to guide in the slide channel 6 and for closing the slide channel 6.
• the Guide outer surfaces 68 and 70 for example, be interrupted by pressure relief grooves, as far as the aforementioned guiding and closing function is not substantially impaired.
• the guide portion 30 is shown, which substantially comprises a guide outer surface, which is not interrupted substantially.
• the guide outer surface of the guide portion 30 may be interrupted, for example by a pressure relief groove, as far as their leadership function is not impaired, especially in the sections 34 and 66 of the slide channel 6.
• the valve spool 10 has the guide portion 30 in the opening portion 20, wherein the guide portion 30 is substantially continuous in the respective
• the cross-sectional recesses 26 and 28 close in cross section to the guide portion 30 and are formed substantially planar.
• control edges 72 and 74 are formed. Between the opening portion 20 and the closing portion 22 control edges 76 and 78 are formed.
• the control edges 72 to 78 have a substantially
• Circular segment line shape wherein a corresponding circular area is aligned substantially transverse to the longitudinal axis 8.
• An end face 84 is aligned in the direction of the arrow 52 and thus in the direction of the actuator. Between the end face 84 and the closing portion 22, the valve spool 10 has a conically shaped, towards the
• End face 84 tapered surface 86 on.
• FIG. 5 shows a section-wise cross-sectional view of the first slide valve 2 according to a transverse surface through the longitudinal axis 8 and through the longitudinal axis 38 of the working pressure connection channel 14 according to FIG. 1, in particular from a direction according to the arrow 52.
• the valve spool 10 in the region of the opening portion 20 substantially has a triangular shape in cross section.
• the guide sections 30, 32 and 90 are in accordance with the respective corresponding inner surface of the
• Slider channel 6 is formed. Between the guide sections 30, 32 and 90 the cross-sectional recesses 28, 88 and 26 extend against the
• the opening portion 20 of the valve spool 10 has an axial symmetry to the axis 38 in cross-section. Furthermore, the opening portion 20 of the valve spool 10 in cross-section on a rotational symmetry, in which a circular segment of 120 ° in the degree by a rotation around a
• Cross-section circle center which is located on the longitudinal axis 8, can be imaged on another circle segment of 120 ° in the degree.
• the cross-sectional recess 88 is in the cross section of the valve spool 10 to the cross-sectional recess 28 in the circumferential direction substantially equidistant spaced as to the cross-sectional recess 26.
• a cross-sectional recess 88 is in the cross section of the valve spool 10 to the cross-sectional recess 28 in the circumferential direction substantially equidistant spaced as to the cross-sectional recess 26.
• Guide portion 30 in the circumferential direction substantially equidistant from the guide portion 90 as spaced from the guide portion 32.
• Cross-sectional recesses 26, 28 and 88 each serve to provide fluid communication in one of the sections 34 and / or 66 of the valve in the open gate position
• FIG. 6 shows, in a schematic sectional view of a second slide valve 92, that, in contrast to the first slide valve 2 from FIGS
• Valve slide 94 has.
• a housing 96 of the second slide valve 92, in contrast to the housing 4 of the first slide valve 2 has no connection between the connection channels 14 and 16.
• a pressure chamber 98 is essentially delimited by the slide channel 6 and the end face 54 of the valve slide 94.
• a longitudinal bore 102 and a transverse bore 104 always provide a fluid connection between the working pressure port 14 and the pressure chamber 98 ago.
• the actuator 54 for the valve spool 94 facing away from the end face 54 of the valve spool 94 is pressurized via the pressure chamber 98 against the direction of the arrow 52 and thus against the actuator direction of action with pressure.
• the longitudinal bore 102 opens into the pressure chamber 98 and the
• Transverse bore 104 which is connected to the longitudinal bore 102 to a fluid connection, opens in the pressure build-up position in the region of the opening portion 20 in the working pressure port 14. According to the arrows 106 and 108 flows in the illustrated pressure build-up fluid from the pressure supply port 16 in the Working pressure connection channel 14.
• FIG. 7 shows, analogously to FIG. 5, a sectional view in accordance with a transverse surface to the longitudinal axis 8 through the axis 38.
• the transverse bore 104 is embodied without a mirroring.
• Figure 8 shows a schematic sectional view of a third slide valve 1 12 in a closed position.
• a valve slide 1 14 is shown in contrast to the figures 1, 2, 3 and 6 in a sectional view.
• the valve spool 1 14 cross-sectional recesses 1 16 and 1 18 on.
• valve slide 1 14 Longitudinal axis 8, the valve slide 1 14 a diameter jump 120, which is explained in more detail to Figure 9 designed as an annular edge.
• a housing 1 12 of the third slide valve 1 12 has according to the diameter jump 120 a
• Slider channel 7 which has a larger diameter in the section 66 than in the section 34.
• the slide channel 7 and the valve slide 1 14 are formed such that the valve slide 1 14 in the open slide position, which is not shown in Figure 8, a Fluid connection between two adjacent ones
• Connecting channels 12 and 14 or 14 and 16 produces and the valve spool 1 14 is guided in the open slide position in a section 34 and / or a portion 66 of the slide channel 7 between the adjacent connection channels 14 and / or 16.
• a space 124 is essentially limited by the slide channel 7 and an end face of the valve slide 1 14, which is aligned opposite to the actuator, not shown.
• the space 124 is connected via a channel 126 in a manner not shown with the fluid tank or with the tank connection channel 12.
• Restoring force against the arrow 52 is produced by means of the change in diameter 120.
• the housing 122 has a recess 128 in the section 34, which corresponds to the change in diameter 120.
• the recess 128 can serve in particular as a stop means for the change in diameter 120.
• FIG. 9 is a perspective view of the opening portion 20 of FIG.
• the opening portion 20 is in a first
• the first opening portion 20a has, with the adjoining, the diameter change 120 opposite closing portion 24 has a smaller diameter than the second opening portion 20b with the subsequent, the Diameter change 120 opposite closing portion 22.
• a guide portion 130 for guiding the valve spool 1 14 in the section 34 continuously in the closing portion 24 via.
• a guide portion 132 is continuously in the second opening portion 20b.
• Partial annular surface 134 is formed, which is formed according to a diameter jump substantially transversely to the longitudinal axis 8 of the valve slide 1 14. A normal vector of the partial annular surface 134 is aligned substantially counter to the arrangement of an actuator for the valve spool 14.
• cross-sectional recesses 16 and 136 extend longitudinally over the
• the cross-sectional recesses 16 and 136 and 118 are concave from the respective control edges 144 and 138 and 142 and 140, respectively.
• H. formed with a curvature inwardly toward the longitudinal axis 8.
• the valve spool 1 14 has four cross-sectional recesses and four guide sections in the opening section 20 in cross-section.
• the valve slide 1 14 may also have more than four cross-sectional recesses in particular six, eight or ten or more cross-sectional recesses.
• the cross-sectional recesses 16 and 136 and 118 are concave from the respective control edges 144 and 138 and 142 and 140, respectively.
• H. formed with a curvature inwardly toward the longitudinal axis 8.
• the valve spool 1 14 has four cross-sectional recesses and four guide sections in the opening section 20 in cross-section.
• the valve slide 1 14 may also have more than four cross-section
• Valve slide 1 14 have more than four guide sections in particular six, eight or ten or more guide sections. These cross-sectional recesses and / or guide portions may in particular be arranged so that in the cross-section of the valve spool essentially results in a point symmetry to a cross-sectional center of the valve spool 1 14, wherein the
• Cross-section center lies on the longitudinal axis 8.
• FIG. 10 shows a fourth slide valve 142 in the pressure reduction position.
• fluid may flow from the working pressure port 14 into the tank port 12 via cross-sectional recesses 150 and 152.
• a valve spool 154 has a diameter change 121 which, in contrast to the diameter change 120 according to FIGS. 8 and 9, is chamfered.
• the diameter change 121 according to FIG. 10 is discontinuous. However, it is also possible to choose continuous versions of the diameter change 121. Overall, a desired restoring force against the actuator force can be adjusted by the choice of the diameter difference in the region of the diameter change 120.
• valve spool 154 has guide sections analogous to the guide sections 130 and 132 of the valve spool 14.

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• Engineering & Computer Science (AREA)
• General Engineering & Computer Science (AREA)
• Mechanical Engineering (AREA)
• Multiple-Way Valves (AREA)
• Sliding Valves (AREA)

Applications Claiming Priority (2)

Publications (1)

Family

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Family Applications (1)

Country Status (7)

Families Citing this family (12)

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• 2013
  • 2013-06-06 DE DE201310210500 patent/DE102013210500A1/de not_active Withdrawn
• 2014
  • 2014-03-11 US US14/896,536 patent/US9874282B2/en not_active Expired - Fee Related
  • 2014-03-11 JP JP2016517194A patent/JP2016520781A/ja active Pending
  • 2014-03-11 CN CN201480032262.4A patent/CN105247259B/zh not_active Expired - Fee Related
  • 2014-03-11 WO PCT/EP2014/054679 patent/WO2014195035A1/de active Application Filing
  • 2014-03-11 KR KR1020157034601A patent/KR20160015242A/ko not_active Application Discontinuation
  • 2014-03-11 EP EP14709281.1A patent/EP3004701A1/de not_active Withdrawn

Non-Patent Citations (1)

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