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WO2018141445A1 - Soupape de limitation de débit et système hydraulique - Google Patents

Soupape de limitation de débit et système hydraulique Download PDF

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Publication number
WO2018141445A1
WO2018141445A1 PCT/EP2017/082240 EP2017082240W WO2018141445A1 WO 2018141445 A1 WO2018141445 A1 WO 2018141445A1 EP 2017082240 W EP2017082240 W EP 2017082240W WO 2018141445 A1 WO2018141445 A1 WO 2018141445A1
Authority
WO
WIPO (PCT)
Prior art keywords
cage
flow
cage portion
section
axial
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.)
Ceased
Application number
PCT/EP2017/082240
Other languages
German (de)
English (en)
Inventor
Jan Spieler
Michael Kuehner
Stefan Kohlhaas
Sven Schuster
Reiner Castan
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.)
Magna PT BV and Co KG
Original Assignee
Getrag BV and Co KG
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 Getrag BV and Co KG filed Critical Getrag BV and Co KG
Publication of WO2018141445A1 publication Critical patent/WO2018141445A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

Links

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
    • F16K17/00—Safety valves; Equalising valves, e.g. pressure relief valves
    • F16K17/20—Excess-flow valves
    • F16K17/22—Excess-flow valves actuated by the difference of pressure between two places in the flow line
    • F16K17/24—Excess-flow valves actuated by the difference of pressure between two places in the flow line acting directly on the cutting-off member
    • F16K17/28—Excess-flow valves actuated by the difference of pressure between two places in the flow line acting directly on the cutting-off member operating in one direction only
    • F16K17/30—Excess-flow valves actuated by the difference of pressure between two places in the flow line acting directly on the cutting-off member operating in one direction only spring-loaded
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D15/00—Control, e.g. regulation, of pumps, pumping installations or systems
    • F04D15/0005—Control, e.g. regulation, of pumps, pumping installations or systems by using valves
    • F04D15/0022—Control, e.g. regulation, of pumps, pumping installations or systems by using valves throttling valves or valves varying the pump inlet opening or the outlet opening
    • 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
    • F16H61/029—Throttle valves
    • G—PHYSICS
    • G05—CONTROLLING; REGULATING
    • G05D—SYSTEMS FOR CONTROLLING OR REGULATING NON-ELECTRIC VARIABLES
    • G05D7/00—Control of flow
    • G05D7/01—Control of flow without auxiliary power
    • G05D7/0126—Control of flow without auxiliary power the sensing element being a piston or plunger associated with one or more springs
    • G05D7/0133—Control of flow without auxiliary power the sensing element being a piston or plunger associated with one or more springs within the flow-path
    • 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
    • F16K2200/00—Details of valves
    • F16K2200/40—Bleeding means in closed position of the valve, e.g. bleeding passages
    • F16K2200/402—Bleeding means in closed position of the valve, e.g. bleeding passages arranged on the valve housing or seat

Definitions

  • the present invention relates to a flow restrictor with a cage which is insertable into a fluid passage and which has a first axial end and a second axial end, and with a locking member which is axially movably mounted on the cage between a locking position and a release position is, and with a spring element which acts between the cage and the blocking element and biases the blocking element in the release position or in the blocking position, wherein the flow limiting valve in the release position of the blocking element defines a first flow cross-section and defines a second flow area in the Spenposition, the smaller is considered the first flow area.
  • the present invention relates to a hydraulic system with a
  • Fluid supply device with a hydraulic consumer and with a flow relief valve of the type specified above.
  • Flow control valves are passive valves, which are controlled and switched solely due to the pressure conditions existing on the valve.
  • such restrictor valves are actuated due to a back pressure at one axial end, the back pressure moving the blocking element from a release position to a blocking position.
  • Body portion having a first end, a second end and an axially extending passage includes.
  • An adjustment valve is provided which is axially movable under the influence of fluid pressure from a rest position to a flow restriction position.
  • Such a flow or flow control valve can be used for example in heating systems. More flow control valves are disclosed in the German
  • a flow relief valve with a cage which is insertable into a fluid channel and which has a first axial end and a second axial end, with a blocking element, which is movable on the cage axially between a locking position and a release position is mounted, and with a spring element which acts between the cage and the blocking element and biases the blocking element in the release position or in the blocking position, wherein the flow limiting valve in the release position of the blocking element defines a first flow cross-section, and defines a second flow cross-section in the blocking position which is smaller than the first flow cross-section, wherein the cage has a first cage portion in the region of the first axial end and a second cage portion in the region of the second axial end, wherein the blocking element comprises a plate and a shaft connected to the plate wherein the shaft is axially slidably mounted on the first cage portion and wherein the plate rests in the locking position on a valve seat on the second cage portion, and wherein the second flow cross section is formed by at
  • Fluid supply device with at least one hydraulic consumer and with a flow-limiting valve of the type according to the invention.
  • the flow-limiting valve according to the invention represents a simple, inexpensive and reliable construction of a flow-limiting valve for actuatorless switching between two different volume flow divisions.
  • the flow-limiting valve according to the invention allows the
  • the spring element is preferably a mechanical spring element, in particular in
  • a compression spring preferably in the form of a helical compression spring, which is arranged around the shaft of the blocking element around.
  • the blocking element is biased in the release position, but it may also be biased in some applications in the locked position.
  • the flow-limiting valve is preferably designed so that it due
  • a fluid pressure or dynamic pressure from the biasing position (preferably the release position) in the other position (preferably the locking position) is pressed, against the force of the spring element.
  • the flow-limiting valve is preferably inserted into a fluid channel so that inflowing fluid flows against the plate of the blocking element, and presses the plate against the valve seat (or in the alternative embodiment of the valve seat dissolves) with build-up dynamic pressure.
  • the first flow cross section is preferably defined by a central flow opening in the second cage section.
  • the first and the second cage section preferably each have a plate-like
  • the second flow cross section is preferably greater than zero, but can in
  • the cage is preferably formed in one piece, in particular from a
  • Plastic material preferably of an injection molding material such as a heat-resistant plastic.
  • the spring element preferably acts between the first cage portion and the
  • the channel passing through the second cage section is preferably an axial channel.
  • the first and the second flow cross-section are preferably not variable
  • the flow-limiting valve is preferably switchable exclusively between two states, namely the blocking position and the release position.
  • the blocking element is guided on a cage, there is the possibility to flow around the locking element even in the release position, so that even in the release position deposits of foreign body can be prevented. Consequently, jamming or fouling of the flow restricting valve can be reduced or prevented.
  • contact surfaces can be reduced and the possibility for foreign body or dirt deposits can be reduced.
  • the flow-limiting valve is preferably in a hydraulic arrangement
  • the second cage portion faces a pressure port of the pump, that is, a feed direction for fluid.
  • the other axial end is preferably connected to a hydraulic consumer.
  • the channel adjacent to a closed in the blocking position flow opening of the valve seat and / or on an outer circumference of the second cage portion is formed.
  • the channel is adjacent to a flow opening of the valve seat, it is particularly preferred if the channel directly adjoins the flow opening, such that the channel and the flow opening are formed by a common opening.
  • a channel for forming the second flow cross section may be formed in the region of an outer circumference of the second cage section, for example by a radial recess on the outer circumference of the second cage section.
  • the channel, which forms the second flow cross-section is formed as a completely independent axial bore in the second cage section, which is connected neither to the outer circumference nor to a central flow opening of a valve seat.
  • the shank has a shank outer diameter in the region of the first cage section, the shank opening through an axial opening extends through the first cage portion, which has an axial opening inner diameter which is larger than the shaft outer diameter.
  • the ratio of outer shaft diameter and Axialö GmbHsinnen bemesser is chosen so that between a clearance or even greater difference is established.
  • the shaft is mounted on the first cage section in such a way that along the shaft path there is no circumferential surface on which friction between the shaft and the cage section could exist.
  • the shaft is mounted on the first cage portion so that it is slightly radially movable in it, so that no dirt particles or the like can accumulate in this area.
  • the game is between
  • Shaft outer diameter and Axialö Anlagensinnen penmesser at least 0.1 millimeters, but preferably an amount between 0.2 and 2 millimeters, but not more than 3 millimeters.
  • a damping of the flow control valve can be adjusted.
  • the diameter ratio of shaft outside diameter to inside axial diameter is in a range between 1: 1, 04 and 1: 1.4.
  • the shaft is axially secured with respect to the first cage section on an axially opposite side of the first cage section to the second cage section.
  • Cage portion a radially elastically deformable locking portion, by means of which the shaft is axially secured with respect to the first cage portion.
  • the stem can be easily mounted with respect to the first cage portion by inserting the stem into an axial opening in the first cage portion.
  • the latching section can be radially compressed until latching tongues or other latching features of the latching section engage behind the axial side of the first cage section, which faces away from the second cage section.
  • the shaft is axially secured with respect to the first cage portion by means of an axial securing ring, which is preferably mounted in a circumferential groove of the shaft.
  • the assembly takes place by the shaft by a
  • Axialö réelle is passed in the first cage portion until the axial securing ring can be inserted into the circumferential groove of the shaft, in order to realize in this way the axial securing.
  • the second cage section has a central one
  • the plate diameter of the blocking element is preferably larger than that
  • the valve seat is formed on the axial side facing away from the first cage portion of the second cage portion and is preferably realized as a flat seat.
  • the diameter of the central flow opening is larger than the diameter of the
  • Shank is preferably also larger than the outer diameter of a spring element which is arranged as a spiral spring around the shaft.
  • the coil spring which acts as a compression spring
  • the coil spring preferably extends through the central flow opening.
  • the second is
  • Caged portion connected to at least one spacer portion, starting from extends from an axial side of the second cage portion opposite the first cage portion in the axial direction and is formed to rest on a shoulder of a fluid channel.
  • the spacer portion preferably has an axial length that is greater than an axial length
  • Spacer sections which are preferably distributed uniformly over the circumference.
  • An outer diameter of the spacer sections is preferably equal to an outer diameter of the second cage section.
  • An inner diameter of the spacer section or of the spacer sections is preferably larger than an outer diameter of the plate of the blocking element.
  • the at least one spacer portion is preferably integral with the cage
  • first cage section and the second cage section are connected to each other via at least one longitudinal web.
  • the longitudinal ridge preferably has an outer diameter which is smaller than a
  • a plurality of longitudinal webs is arranged distributed over the circumference, preferably evenly distributed.
  • An inner diameter of the at least one longitudinal web is preferably greater than or equal to a diameter of a central flow opening in the second cage section.
  • One Outer diameter of the at least one longitudinal web is preferably smaller than an outer diameter of the cage sections.
  • Fluid supply device comprises a driven by an electric motor pump, wherein the flow limiting valve between a pressure port of the pump and the hydraulic consumer is arranged.
  • a switching of the flow limiting valve can be initiated such that either one hydraulic consumer or the other hydraulic consumer each more hydraulic fluid per unit time (a larger flow rate) is provided.
  • the first hydraulic consumer which is connected via the flow-limiting valve to the pump, is preferably an electric drive machine of a motor vehicle drive train.
  • the further hydraulic consumer is preferably a wet-running multi-plate clutch of the drive train.
  • Fig. 1 is a schematic representation of an embodiment of a hydraulic arrangement according to the invention
  • Fig. 2 is a schematic representation of a drive train of a motor vehicle, in which the hydraulic arrangement of Figure 1 is used ..;
  • volume flow (for example in l / min) over a rotational speed n of a drive motor of a pump of a fluid supply device
  • Fig. 4 is a schematic perspective view of an embodiment of a
  • FIG. 5 shows a schematic longitudinal sectional view through the flow-limiting valve of FIG. 4 in a fluid channel of a housing, specifically in the release position;
  • FIG. 6 shows the flow-limiting valve of FIGS. 4 and 5 in a blocking position
  • FIG. 7 shows a detailed view VII of FIG. 6.
  • Fig. 1 is an embodiment of a hydraulic arrangement according to the invention
  • the hydraulic assembly 10 includes a fluid supply device 12 configured to provide a total variable fluid flow Q G.
  • the hydraulic assembly 10 further includes a distribution device 14 configured to divide the total fluid volume flow Q G provided by the fluid supply device 12 into one first fluid volume flow Q for a first hydraulic consumer 16 and a second fluid volume flow Q 2 for a second hydraulic consumer 18.
  • the first hydraulic consumer 16 is preferably an electrical
  • the second hydraulic consumer 18 is preferably a wet-running multi-plate clutch of a drive train of a motor vehicle.
  • Fig. 1 schematically as diaphragms or hydraulic
  • the ratio of the fluid volume flows Qi, Q 2 is significantly dependent on the hydraulic resistors R 1 f R 2 , which are set up in a first fluid path or a second fluid path, in which the fluid volume flows Qi and Q 2 are performed.
  • the fluid supply device 12 has a pump 20 which is designed as unidirectional
  • the Pump may be formed, but may also be designed as a bidirectional pump.
  • the pump 20 has a suction port connected to a fluid sump 22 or other low pressure fluid source. Further, the pump 20 includes a pressure port to which the total fluid volume flow Q G is provided.
  • the pump 20 is driven by an electric motor 24 which rotates at a speed n, wherein the speed n can be variably adjusted. Consequently, the total volume flow Q G can be variably adjusted.
  • a flow-limiting valve or Fluidvolumenstrombe- limiting valve 30 is arranged.
  • this flow-limiting valve 30 is switched over from a first valve position (in particular a release position) into a second valve position (in particular a blocking position).
  • the flow through the flow-limiting valve 30 is at a value below that volume flow rate. Limits that has flowed through the flow limiting valve 30 before reaching the limiting volume flow.
  • the ratio Q, IQ 2 may vary from first to second fluid flow alone
  • the first hydraulic consumer 16 is preferably provided with a larger volume flow, so that Qi> Q 2 .
  • the flow limiting valve 30 is in the second valve position (blocking position), it is preferable that Q 2 > Q1.
  • a drive train 40 is shown for a motor vehicle, which has a first
  • Drive motor 42 for example, in the form of an internal combustion engine includes, and a clutch assembly 44, which may be formed as a single or double clutch assembly, but preferably at least one wet-running multi-plate clutch includes.
  • An output of the clutch assembly 44 is connected to an input of a gear assembly 46.
  • An output of the gear assembly 46 is connected to a differential 48, by means of which drive power can be distributed to driven wheels 50L, 50R.
  • the powertrain 40 further includes an electric machine 52 operable as a drive motor to provide drive power to the motor vehicle.
  • the drive train 40 has a hydraulic arrangement 10 which is suitable for the
  • the electric machine 52 provides a first cooling fluid volume flow Qi, and provides a second fluid volume flow Q 2 for the wet-running multi-plate clutch of the clutch assembly 44.
  • the hydraulic assembly 10 of Fig. 2 may preferably correspond in structure and operation to the hydraulic assembly 10 described with reference to Fig. 1.
  • Fig. 3 shows the operation of a flow-limiting valve 30, as shown in the
  • Fig. 3 shows a diagram of Volume flow (for example in l / min) over the speed n of the electric motor 24, which drives the pump 20.
  • the total volume flow Q G increases linearly as the speed n of the pump 20 increases.
  • Distributor 14 is divided into a first fluid volume flow Qi and a second fluid volume flow Q 2 , wherein Qi is greater than Q 2 .
  • the first fluid volume flow C exceeds a restriction fluid volume flow Q s , causing the flow restriction valve 30 to be switched from a first valve position (release position) to a second valve position (lock position).
  • the first fluid volume flow is limited, in such a way that the total fluid volume flow Q G is now divided into a smaller first fluid volume flow Qi and a larger second fluid volume flow Q 2 .
  • wet running multi-plate clutch of the clutch assembly 44 is supplied, abruptly increase in order to provide a high cooling capacity in the event of a brief slipping operation.
  • FIGS. 4 to 7 show an embodiment of a flow-limiting valve 30
  • the flow restriction valve 30 generally corresponds in construction and operation to the flow restriction valve 30, as described above with reference to FIGS. 1 to 3. The same elements are therefore identified by the same reference numerals. The following section essentially explains the differences.
  • the pressure limiting valve 30 of FIGS. 4 to 7 has a cage 60.
  • the cage 60 includes a first cage portion 62, which may be in the form of, for example, an annular disc having an outer diameter that conforms to an inner diameter of a fluid channel into which the cage 60 is to be inserted.
  • the first cage portion 62 has a first axial side 64 and a second axial side 66.
  • the cage 60 includes a second cage portion 68, also in shape
  • a disc may be formed, whose outer diameter is adapted to an inner diameter of a fluid channel.
  • the second cage portion 68 is preferably aligned parallel to the first cage portion 62 and has a first axial side 70 facing the second axial side of the first cage portion 62 and a second axial side 72 facing away from the first cage portion 62.
  • the first cage portion 62 and the second cage portion 68 are over a plurality of
  • the longitudinal webs 74 in which it is preferably about the three as shown
  • Perimeter evenly distributed arranged longitudinal webs each extending in the circumferential direction over less than 60 °, such that in the circumferential direction between the longitudinal webs each radial openings are arranged, which preferably extend over a peripheral portion of more than 60 °.
  • the longitudinal webs 74 have an outer diameter which is smaller than the outer diameter of the cage sections 62, 68.
  • the number of spacer sections 76 is preferably 3.
  • the spacer sections 76 are preferably arranged evenly spaced over the circumference of the cage 60 and preferably extend over each other a circumferential angle of less than 60 °, such that intermediate portions are formed between the spacer portions 76, which extend over more than 60 °.
  • the spacer portions 76 extend over an axial distance L2, preferably
  • An outer periphery of the spacer portions 76 is preferably equal to an outer periphery of the second cage portion 68.
  • the cage 60 with the cage sections 62, 68 and with the longitudinal webs 74 is
  • the spacer sections 76 are preferably formed integrally with the cage 60.
  • the cage 60 with the longitudinal webs 74 and the spacer portions 76 is preferably made of an injection molded plastic material. However, the cage 60 may also be made of a metal material and formed into the desired shape by machining or sintering.
  • the flow restricting valve 30 further includes a blocking member 80.
  • Locking element 80 has a longitudinally extending shaft 82 with a diameter D1 (see FIG. 5). Further, the locking member 80 includes a plate 84 which is preferably circular in shape and has a larger diameter than the shaft diameter D1. The plate 84 and the shaft 82 are preferably integrally connected to each other.
  • the blocking element 80 is longitudinally displaceable in the axial direction with respect to the first
  • the first cage portion 62 has a central axial opening 86 which has an inner diameter D2 which is larger than the outer diameter D1 shank.
  • the ratio of D1 to D2 is selected so that a clearance fit is established between the first cage portion 62 and the shaft 82.
  • the shaft 82 extends through the central axial opening 86 on a side facing away from the second cage portion 68 side of the first cage portion 62. In this area, the shaft 82 is axially secured with respect to the first cage portion 62.
  • An axial securing is indicated schematically in FIG. 4 and in FIG. 5 at 88.
  • the axial securing 88 may, as shown in FIGS. 4 and 5, be formed by a latching portion 90.
  • the latching portion 90 is formed so that the shaft 82 can be radially compressed in this area, for example by a longitudinal recess in the shaft 82, as is indicated schematically in Fig. 5.
  • the latching section 90 preferably includes radially protruding latching tongues 92.
  • the shaft 82 can be inserted into the central axial opening 86 with its end on which the latching section 90 is formed, wherein the latching section is radially compressed in the axial opening 86 due to the latching tongues 92 until the latching tongues 92 engage behind the first axial side 64 of the first cage section 62.
  • the latching portion 90 relaxes, whereby the shaft 82 is secured axially with respect to the first cage portion 62.
  • the shaft 82 is passed through the axial opening 86, and the portion of the shaft projecting from the second axial side 66 includes the circumferential groove into which the axial securing ring 94 can be inserted to secure the shaft 82 axially with respect to the first cage portion 62.
  • the shaft 82 extends from the first cage portion 62 towards the second cage portion 68.
  • a coil spring 96 is disposed, which is supported on the one hand on the second axial side 66 of the first cage portion 62.
  • the coil spring 96 is supported on the plate 84, in particular on a plate surface 98, which faces the first cage portion 62.
  • the shaft 82 extends through a central flow opening 102 in the second
  • a flat valve seat 100 is formed on the second axial side 72 of the second cage section 68 about the central flow passage 102, against which the face plate 98 abuts in a locking position SP, as shown in FIG.
  • the distance between the disc surface 98 and the valve seat 100 in the release position is established by the axial lock 88.
  • the dimension of the locking element 80 with respect to the cage 60 is selected so that in the release position FP shown in FIGS. 4 and 5, the plate surface 98 of the plate 84 axially opposite the valve seat 100 and the second axial side 72 of the second Cage section 68 is spaced.
  • Fiuidvolumenstrom consequently pass between the spacer portions 76 and pass between the plate 84 and the second cage portion 68 in the area between the cage sections 62, 68, as indicated in Fig. 5 by arrows.
  • a reduced flow cross section is established, which is formed by at least one channel 104.
  • the channel 104 is, as shown in FIGS. 5, 6 and 7, immediately adjacent to the central flow opening 102 and formed so that a flow cross-section is set which is smaller than the flow cross-section which is set in the release position FP ,
  • the flow restriction valve 30 allows in the
  • FIG. 5 shows, in a schematic form, a typical installation position of the flow-limiting valve 30 in a housing 110 of a hydraulic system.
  • the housing 110 has a fluid channel 112 which has an inner diameter which corresponds to the outer diameter of the cage sections 62, 68. Further, the fluid channel 112 includes a shoulder 114 through which a transition to a smaller inner diameter is defined.
  • the flow restriction valve 30 is inserted into the fluid channel 112 until the spacer portion 76 abuts the shoulder 114.
  • Radial channel 116 of the housing connected, which is connected to the fluid passage 112.
  • a closure assembly 118 is provided which seals the fluid channel 112 from the environment and secures the flow restriction valve 30 in position adjacent the shoulder 114.
  • FIG. 7 shows that the channel 104, by means of which the second flow cross-section 108 is established, can be formed directly adjacent to the central flow opening 102 in order to allow the second flow cross-section fluid flow 108 ,
  • Fig. 7 is also shown that such a channel 104 'adjacent to a
  • Outer periphery 120 of the second cage portion 68 may be formed, in addition to or as an alternative to the channel 104, so that a second flow cross-section fluid flow 108 'may be established via the channel 104'.
  • the channel 104 ' In the installed position, the channel 104 'preferably lies downwards in the direction of gravity, so that impurities present in a lower region of the fluid channel 112 due to gravity can not settle there, but can be flushed out via the fluid flow 108'. However, it is also conceivable to arrange the channel 104 'preferably in the direction of gravity at the top so that no impurities can settle in the region of the channel 104' at all.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • General Physics & Mathematics (AREA)
  • Automation & Control Theory (AREA)
  • Sliding Valves (AREA)

Abstract

L'invention concerne une soupape de limitation de débit (30) comprenant une cage (60) qui peut être insérée dans un conduit de fluide (112) et qui comprend une première extrémité axiale et une deuxième extrémité axiale, un élément de blocage (80) qui est monté sur la cage de manière déplaçable axialement entre une position de blocage (SP) et une position de libération (FP), et un élément ressort (96) qui agit entre la cage et l'élément de blocage et précontraint l'élément de blocage dans la position de libération ou dans la position de blocage, la soupape de limitation de débit définissant, dans la position de libération de l'élément de blocage, une première section transversale de débit (106) et définissant, dans la position de blocage, une deuxième section transversale de débit (108) qui est plus petite que la première section transversale de débit, la cage comprenant une première partie de cage (62) dans la région de la première extrémité axiale et une deuxième partie de cage (68) dans la région de la deuxième extrémité axiale, l'élément de blocage comprenant un plateau (84) et une tige (82) reliée au plateau, la tige étant montée de manière axialement mobile sur la première partie de cage et le plateau s'appuyant contre un siège de soupape (100) sur la deuxième partie de cage dans la position de blocage, et la deuxième section transversale de débit étant formée par au moins un conduit (104) qui traverse la deuxième partie de cage.
PCT/EP2017/082240 2017-01-31 2017-12-11 Soupape de limitation de débit et système hydraulique Ceased WO2018141445A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102017101826.3 2017-01-31
DE102017101826.3A DE102017101826A1 (de) 2017-01-31 2017-01-31 Durchflussbegrenzungsventil und Hydraulikanordnung

Publications (1)

Publication Number Publication Date
WO2018141445A1 true WO2018141445A1 (fr) 2018-08-09

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PCT/EP2017/082240 Ceased WO2018141445A1 (fr) 2017-01-31 2017-12-11 Soupape de limitation de débit et système hydraulique

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WO (1) WO2018141445A1 (fr)

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CN111853245A (zh) * 2019-04-24 2020-10-30 艾欧史密斯(中国)热水器有限公司 阀门及其控制方法、过滤水装置及其控制方法
WO2025255925A1 (fr) * 2024-06-13 2025-12-18 金华市威科工贸有限公司 Machine de récupération de fluide frigorigène

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DE102022214389A1 (de) 2022-12-23 2024-07-04 Magna powertrain gmbh & co kg Anordnung und Verfahren zur bedarfsgerechten Verteilung von Kühl-/Schmierölströmen im elektrischen Traktionsantrieb
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