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EP1540191B1 - Soupape a commande hydraulique pourvue d'au moins une unite de commande hydraulique - Google Patents

Soupape a commande hydraulique pourvue d'au moins une unite de commande hydraulique Download PDF

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Publication number
EP1540191B1
EP1540191B1 EP04738137A EP04738137A EP1540191B1 EP 1540191 B1 EP1540191 B1 EP 1540191B1 EP 04738137 A EP04738137 A EP 04738137A EP 04738137 A EP04738137 A EP 04738137A EP 1540191 B1 EP1540191 B1 EP 1540191B1
Authority
EP
European Patent Office
Prior art keywords
valve
control
control pressure
pressure chamber
pressure
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.)
Revoked
Application number
EP04738137A
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German (de)
English (en)
Other versions
EP1540191A1 (fr
Inventor
Josef ZÜRCHER
Hansruedi Brand
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.)
Bucher Hydraulics AG
Original Assignee
Bucher Hydraulics AG
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Filing date
Publication date
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/003—Systems with load-holding valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B13/01—Locking-valves or other detent i.e. load-holding devices
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B21/00—Common features of fluid actuator systems; Fluid-pressure actuator systems or details thereof, not covered by any other group of this subclass
    • F15B21/008—Reduction of noise or vibration
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/50—Pressure control
    • F15B2211/505—Pressure control characterised by the type of pressure control means
    • F15B2211/50509—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means
    • F15B2211/50545—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means using braking valves to maintain a back pressure

Definitions

  • the invention relates to a hydraulically controlled valve with at least one hydraulic drive according to the preamble of claim 1.
  • a load-holding brake valve which is controllable by a hydraulic drive.
  • the main piston of the load-holding brake valve is actuated by a plunger of a control piston.
  • This control piston is moved against the pressure of a Auf Kunststofffeder by a control pressure.
  • load-holding brake valves are suitable, for example, for controlling double-acting hydraulic consumers which are mechanically loaded. Depending on the type of mechanical stress, such devices tend to vibrate. For example, arrangements with a very long lever arm are known, for example in cranes. For example, a shock can cause a vibration through which the volume flow of the hydraulic oil fluctuates.
  • vibrations can also be triggered in the hydraulic system itself, when the control of a movement is started and / or the movement is accelerated or decelerated. Due to such vibrations, the speed of the hydraulic consumer is no longer constant. In this way, a precise control of movements is difficult or even prevented.
  • a directional control valve which is suitable for controlling double-acting hydraulic consumers. It is disclosed here that the spool of the directional control valve is movable by at least one drive. Shown is also a solution with two hydraulic drives. In each of these drives is arranged by a control pressure against a spring movable drive piston. Through this, for example, via a piston rod of the spool of the directional control valve movable. Vibration problems can also arise in such arrangements.
  • the invention has for its object to provide a hydraulically controlled by at least one hydraulic actuator valve, which against internal or external triggered vibrations is insensitive, without the responsiveness is deteriorated.
  • Fig. 1 which is a schematic representation, 1 means a hydraulically controlled valve, which in this embodiment is a load-holding brake valve.
  • This designed as a load-holding brake valve hydraulically controlled valve 1 is shown on the right in a view that reveals no details of the internal structure, because the internal structure is not essential to the invention and in itself from WO-A1-97 / 32136 known.
  • the waiver of the representation of this internal structure is also appropriate because the not essential to the invention parts of the hydraulically controlled valve 1 may well be constructed differently than shown and described in WO-A1-97 / 32136.
  • the invention is therefore independent of a particular type of load-holding brake valve and regardless of the design of the valve 1.
  • valve 1 is hydraulically controlled by at least one hydraulic drive and that the valve 1 has a flow control device 2 through the flow of hydraulic oil from and to a consumer is controllable.
  • This flow control device 2 is controlled by a hydraulic drive 3.
  • a control plunger 4 which is part of a control piston 5, which acts on the flow control device 2.
  • the valve 1 is a load-holding brake valve, also called a lowering brake valve
  • the flow control device 2 consists, for example, of a pilot valve and a main valve.
  • the control plunger 4 acts directly on a spool.
  • the control piston 5 is shown as a view. According to the invention, it is designed as a stepped piston whose features according to the invention are described below. It should be mentioned in advance that on the left of the valve 1, a control pressure port X is provided on a housing part 6. At the control pressure port X in the housing part 6, a bore is present, which is referred to here as the control pressure primary chamber 7.
  • the control piston 5 at its the control pressure port X facing the end of a first stage 8, whose diameter D 8 only so much smaller than the inner diameter of the control pressure primary chamber 7, that he can move.
  • a control pressure Px present at the control pressure connection X and thus acting in the control pressure primary chamber 7 thus exerts a force F on the control piston 5 which corresponds to the product of the control pressure P x and the end face A 8 of the first stage 8, the end face A 8 the first stage 8 is the product of half diameter D 8 squared and ⁇ .
  • the control pressure P x thus causes a force F, with which the control piston 5 is pressed against a control spring 9. In this case, the path traveled by the control piston 5 depends on the spring rate of the control spring 9.
  • control piston 5 has a second step 10 whose diameter D 10 is greater than the diameter D 8 .
  • the diameter D 10 is slightly smaller than the inner diameter of a bore in the housing part 6. This bore in the housing part 6 is referred to as control pressure secondary chamber 11.
  • the hydraulically additionally effective area A 10 of the second stage 10 is a circular ring with the outer diameter D 10 and the inner diameter D. 8
  • Essential to the invention is that the control pressure primary chamber 7 and the control pressure secondary chamber 11 are connected by a connection 12 with a throttle point 13, which is shown schematically in FIG. It is irrelevant whether these control pressure primary chamber 7 and the control pressure secondary chamber 11 are formed by bores in a housing part 6 or whether they are realized in another way. An alternative embodiment will be shown. Essential to the invention is only that the hydraulic drive 3, the control pressure primary chamber 7 and the control pressure secondary chamber 11 has.
  • a higher control pressure P X acts only on the smaller end face A 8 .
  • the higher control pressure P X also acts on the hydraulically effective surface of the second stage 10, ie in total on an area A 10 , which results directly from the diameter D 10 . It follows that the movement of the control piston 5 is delayed, that is damped. In this way, the object of the invention is achieved in a surprisingly simple manner, because by this damping, the valve 1 against internal or external induced vibrations insensitive, without the responsiveness is deteriorated, which is when using a metering valve according to WO-A1-97 / 32136 could not be ruled out.
  • the diameter D 8 is for example 14 mm, the diameter D 10 20 mm.
  • the hydraulically effective end faces A 8 and A 10 are respectively 153.9 and 314.2 mm 2 , which gives an area ratio of 1 to 2.04. This indicates how large the amplitude of adjustable vibrations can be.
  • control pressure P X With decreasing control pressure P X , the damping is effective in an analogous manner. If the control pressure P X is reduced, the pressure in the control-pressure secondary chamber 11 can only be reduced slowly by hydraulic oil flowing via the connection 12 to the throttle point 13 from the control-pressure secondary chamber 11 into the control-pressure primary chamber 7.
  • the first stage 8 of the control piston 5 in conjunction with the associated bore in the housing part 6, which forms the control pressure primary chamber 7, are used.
  • the control pressure primary chamber 7 has an inner diameter D 7 .
  • the first stage 8 of the control piston 5 has, as already shown in Fig. 1, an outer diameter D. 8 This results in between an annular gap 14, the dimensions of which are given by the inner diameter D 7 and the outer diameter D 8 . If this annular gap 14 is used as a throttle 13, so that has a remarkable advantage.
  • annular gap 14 Since the annular gap 14 is functionally essential, the tolerances of inner diameter D 7 and outer diameter D 8 is of great importance. These tolerances are chosen so that the annular gap 14 has a gap height of advantageously about 0.01 mm to 0.04 mm. In order to achieve this, a pairing of control piston 5 and housing part 6 can optionally be carried out by selecting mutually compatible production parts.
  • FIGS. 3a to 3c show a hydraulic circuit with a consumer 20, which in the illustrated example is a double-acting cylinder with a bottom pressure chamber and a rod pressure chamber. Instead of the double-acting cylinder but also a hydraulic motor 20 can be operated as a consumer.
  • the hydraulic circuit is shown in three operating states, namely in the neutral position in FIG. 3a, in the load-lifting mode in FIG. 3b and in the load-reducing mode in FIG. 3c.
  • the existing individual elements of the hydraulic circuit are the same in all cases.
  • the hydraulic circuit is known per se and is shown here, because can be described with reference to this circuit, the inventive effect of the inventively designed hydraulically controlled valves.
  • a directional control valve 21 and a load-holding brake valve 22 are shown, which serve to control the load 20.
  • the load-holding brake valve 22 may, for example, be of the type shown in WO-A1-97 / 32136, but is equipped with a hydraulic drive 3 designed according to the invention.
  • the directional control valve 21 may, for example, be of one of the designs shown in WO-A1-02 / 075162, but is also equipped with hydraulic drives 3 'designed according to the invention.
  • the hydraulic oil can be conveyed between the tank 25 and the consumer 20 by means of a pump 24 driven by a motor 23.
  • the pump 24 are associated in a known manner, a first check valve 26 and a pressure relief valve 27.
  • the flow of the hydraulic oil is determined by the positions of the directional control valve 21 and the load-holding brake valve 22.
  • a second check valve 28 is arranged in a line to the bottom pressure chamber of the consumer 20, .
  • This separate check valve 28 can be omitted if the load-holding brake valve 22 includes such a check valve, which is in the representation of the load-holding brake valve 22 by the reference numeral 28 'is designated.
  • the directional control valve 21 is controlled in a known manner that its two drives 3 'are controlled. If none of the drives 3 'are actuated, ie acted upon by a control pressure P St , the directional control valve 21 assumes the neutral position.
  • Fig. 3b the load-lifting operation is shown. This is achieved in that the one of the drives 3 'of the directional control valve 21 is driven with a control pressure P St. The spool of the directional control valve 21 is thereby moved so that the flow of hydraulic oil from the pump 24 through the directional control valve 21 to the bottom pressure chamber of the consumer 20 and from the rod pressure chamber of the consumer 20 to the tank 25 is possible. The pump 24 thus delivers hydraulic oil from the tank 25 to the bottom side of the consumer 20, wherein the first check valve 26 and the second
  • Fig. 3c the load lowering operation is shown.
  • the pump 24 delivers hydraulic oil to the rod-pressure chamber of the consumer 20.
  • the other drive 3 'of the directional control valve 21 is acted upon by a control pressure P St.
  • P St the control pressure
  • the connection from the pump 24 to the rod pressure chamber of the consumer 20 is open and also the connection from the bottom pressure chamber of the consumer 20 to the tank 24.
  • the control pressure P X acting on the load-holding brake valve 22 is now high. It is determined by the pressure generated by the pump and the pressure loss across the directional control valve 21.
  • FIG. 4 shows an advantageous embodiment of a drive 3 which can be used in the case of a load-holding brake valve 22 (FIGS. 3 a to 3 c).
  • Fig. 4 corresponds to the Fig. 1, but also contains this advantageous embodiment. This is that between the control pressure primary chamber 7 and the control pressure secondary chamber 11, a relief check valve 30 is arranged. This allows the pressure reduction from the Steuerdruek secondary chamber 11 to the control pressure primary chamber 7 out, the pressure difference at which the relief check valve 30 opens, is determined by a spring 31.
  • This relief check valve 30 has the effect described below. If the control pressure P X is reduced, as has already been mentioned initially, the control piston 5 is moved to the left by the action of the control spring 9. This means first that the pressure in the control pressure secondary chamber 11 can not fall immediately. The pressure drop can only under the effect of compound 12 with the Throttling point 13 occur. In the load-lifting state according to FIG. 3b, however, as previously stated, the load-holding brake valve 22 has no effect. It is therefore not useful if the damping effect occurs in this operating state by the inventive design of the drive 3. By the relief check valve 30, this is achieved.
  • Fig. 5 which in itself corresponds to FIG. 4, but in which instead of the connection 12 with the throttle point 13 of the annular gap 14 is shown, it is shown as an additional advantageous embodiment that in the cylindrical surface of the first stage 8 at the Control pressure secondary chamber 11 facing a longitudinal groove 33 is inserted.
  • the effective length of the annular gap 14 is limited, the flow of hydraulic oil between the control pressure primary chamber 7 and the control pressure secondary chamber 11 facilitates and thus limits the effect of the damping.
  • the damping effect of a valve 1 with respect to the particular application can be very easily adjusted by the length of the longitudinal groove 33 is chosen differently depending on the application.
  • FIG. 6 shows a further advantageous embodiment of a drive 3 which can be used in the case of a load-holding brake valve 22 (FIGS. 3 a to 3 c).
  • the relief check valve 30 shown in FIGS. 4 and 5 is integrated directly into the drive 3. Shown are only the functionally important parts according to the invention, but not, for example, those parts that serve the power transmission to the operated Fluß complaintvornchtung 2 (Fig. 1), not the control spring 9 ( Figure 1).
  • the control piston 5 Shown is the control piston 5 with its first stage 8 and its second stage 10, which, as previously shown, the diameter D 8 and D 10 have. Also shown are the control pressure primary chamber 7 and the control pressure secondary chamber 11. Notwithstanding FIG. 5, in this exemplary embodiment the relief check valve 30 is arranged within the hydraulic drive 3. In contrast to the embodiments according to FIGS. 1, 4 and 5, the hydraulic drive 3 has no special housing part 6. Instead, the hydraulic drive 3 is arranged inside the housing of the valve 1 to be controlled (FIG. 1), this housing being designated by the reference numeral 40 in FIG. In the left open housing 40, a lid 41 is screwed. In this cover 41 is an opening which represents the control pressure port X, which, as in the previous embodiments, is connected to the control pressure primary chamber 7.
  • an aperture 42 is now arranged between the control pressure connection X and the control pressure primary chamber 7, namely within the cover 41.
  • a limitation of the flow is achieved. This has the consequence that at rapidly increasing control pressure P X, the increase in the pressure in the control pressure primary chamber 7 is delayed. Since this delay of the pressure increase means a damping, this means an advantageous additional measure with regard to the solution of the problem.
  • the damping according to the invention by the throttle point 13 (FIG. 1) or the annular gap 14 and the damping by the aperture 42 additionally acts, it is advantageous if the attenuation by the aperture 42 is significantly lower than the damping by the throttle 13 It has been found that an optimal effect then results if, for example, the annular gap 14 is dimensioned so that it corresponds to a nozzle of 0.1 mm diameter, while the diaphragm 42 a Nozzle diameter of 0.3 to 0.6 mm corresponds. With a diameter ratio of 1: 3 to 1: 6 results in an area ratio of 1: 9 to 1:36. This clearly shows that the damping through the throttle point 13 (FIG. 1) or the annular gap 14 is dominant. Through the aperture 42, a further improvement is achieved
  • the relief check valve 30 integrated in the hydraulic drive 3 is formed by a non-return plate 45 which seals against a seat surface 44 and is pressed against the seat surface 44 by the spring 31 already shown in FIGS. 4 and 5.
  • the check disc 45 has a central bore 46. Within this bore 46 is that part of the control piston 5, which forms the first stage 8.
  • the annular gap 14 is thus limited on the one hand by this bore 46 and on the other hand by the diameter D 8 of the first stage 8 of the control piston 5. With regard to the dimensioning of the annular gap 14, the rules already mentioned are applicable.
  • the function of this relief check valve 30 has been previously described. 6, the closed position is shown.
  • the relief check valve 30 opens when the control pressure P X is reduced, as has already been described in connection with FIG. 4.
  • the check disc 45 then moves against the spring 31 to the left, so lifts off from the seat 44.
  • hydraulic oil can flow directly from the control pressure secondary chamber 11 into the control pressure primary chamber 7.
  • the relief check valve 30 is parallel to the annular gap 14 between the control pressure primary chamber 7 and the control pressure secondary chamber 11. This is also in the embodiment of FIG. 6 so.
  • the construction according to FIG. 6 advantageously results in a compact construction.
  • the invention is applicable to all types of hydraulically controlled valves 1, if due to the control and / or powered by the consumer 20 Device such as a crane, or a shovel, the occurrence of vibrations can not be excluded.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Analytical Chemistry (AREA)
  • Chemical & Material Sciences (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Valve Device For Special Equipments (AREA)
  • Sliding Valves (AREA)
  • Safety Valves (AREA)
  • Actuator (AREA)
  • Servomotors (AREA)

Claims (10)

  1. Soupape (1) à commande hydraulique pourvue d'au moins un entraînement hydraulique (3 ; 3') comportant un piston pilote (5) auquel est relié un coulisseau de commande (4) agissant sur un dispositif (2) de commande du flux parcourant ladite soupape (1), lequel permet de commander le flux d'huile hydraulique respectivement en provenance et en direction d'un appareil consommateur (20), ledit piston pilote (5) pouvant être mis en mouvement par une pression pilote PX régnant au niveau d'un raccord (X) de pression pilote, en opposition à un ressort de commande (9), caractérisée par le fait que
    - le piston pilote (5) est un piston étagé,
    - qui présente un premier gradin (8) ayant un diamètre D8, sa face extrême A8 étant directement exposée à la pression pilote PX, et
    - qui présente un second gradin (10) ayant un diamètre D10 et une face extrême A10 hydrauliquement opérante ;
    - par le fait que l'entraînement hydraulique (3 ; 3') comprend une chambre primaire (7) à pression pilote et une chambre secondaire (11) à pression pilote,
    - la face extrême A8 du premier gradin (8) étant exposée à la pression régnant dans ladite chambre primaire (7) à pression pilote, et
    - la face extrême A10 du second gradin (10) étant exposée à la pression régnant dans ladite chambre secondaire (11) à pression pilote ;
    - et par le fait qu'une liaison (12), munie d'un étranglement (13), est établie entre la chambre primaire (7) à pression pilote et la chambre secondaire (11) à pression pilote.
  2. Soupape (1) selon la revendication 1, caractérisée par le fait que la liaison (12), munie de l'étranglement (13), est matérialisée par un interstice annulaire (14) qui est défini par le diamètre intérieur de la chambre primaire (7) à pression pilote et par le diamètre D8 du premier gradin (8) du piston pilote (5).
  3. Soupape (1) selon la revendication 2, caractérisée par le fait que l'interstice annulaire (14) possède une hauteur de 0,01 mm à 0,04 mm.
  4. Soupape (1) selon la revendication 2 ou 3, caractérisée par le fait que ladite soupape (1) est une soupape de freinage (22) à maintien de charge.
  5. Soupape (1) selon la revendication 2 ou 3, caractérisée par le fait que ladite soupape est une soupape (21) à plusieurs voies.
  6. Soupape (22) selon la revendication 4, caractérisée par le fait qu'un clapet antiretour de décharge (30), interposé entre la chambre primaire (7) à pression pilote et la chambre secondaire (11) à pression pilote, provoque la suppression de pression s'instaurant vers ladite chambre primaire (7) à pression pilote à partir de ladite chambre secondaire (11) à pression pilote.
  7. Soupape (22) selon la revendication 6, caractérisée par le fait que la différence de pression, en présence de laquelle le clapet antiretour de décharge (30) s'ouvre, peut être déterminée par l'intermédiaire d'un ressort (31).
  8. Soupape (1 ; 21 ; 22) selon l'une des revendications 3 à 7, caractérisée par le fait qu'une saignée longitudinale (33) est pratiquée dans la surface de l'enveloppe cylindrique du premier gradin (8), à l'extrémité tournée vers la chambre secondaire (11) à pression pilote.
  9. Soupape (22) selon la revendication 6 ou 7, caractérisée par le fait que le clapet antiretour de décharge (30) est logé à l'intérieur de l'entraînement hydraulique (3), entre la chambre primaire (7) à pression pilote et la chambre secondaire (11) à pression pilote.
  10. Soupape (22) selon la revendication 9, caractérisée par le fait qu'un diaphragme (42) est interposé entre le raccord (X) de pression pilote et la chambre primaire (7) à pression pilote.
EP04738137A 2003-08-27 2004-08-10 Soupape a commande hydraulique pourvue d'au moins une unite de commande hydraulique Revoked EP1540191B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
CH146503 2003-08-27
CH14652003 2003-08-27
PCT/CH2004/000498 WO2005021978A1 (fr) 2003-08-27 2004-08-10 Soupape a commande hydraulique pourvue d'au moins une unite de commande hydraulique

Publications (2)

Publication Number Publication Date
EP1540191A1 EP1540191A1 (fr) 2005-06-15
EP1540191B1 true EP1540191B1 (fr) 2006-01-11

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ID=33315353

Family Applications (1)

Application Number Title Priority Date Filing Date
EP04738137A Revoked EP1540191B1 (fr) 2003-08-27 2004-08-10 Soupape a commande hydraulique pourvue d'au moins une unite de commande hydraulique

Country Status (6)

Country Link
US (1) US20060011875A1 (fr)
EP (1) EP1540191B1 (fr)
JP (1) JP2006515661A (fr)
AT (1) ATE315729T1 (fr)
DE (2) DE20314232U1 (fr)
WO (1) WO2005021978A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN111397894A (zh) * 2020-04-24 2020-07-10 刘勇 一种换挡定压阀污染耐受性能试验系统

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Publication number Priority date Publication date Assignee Title
JP5666202B2 (ja) * 2010-08-20 2015-02-12 太平電業株式会社 油圧ジャッキの回路構造
CN103291980A (zh) * 2013-06-09 2013-09-11 山东派克诺尔机器有限公司 气控液压单向阀
CN106438536B (zh) * 2016-08-30 2018-04-27 北京精密机电控制设备研究所 一种可扩展高可靠液压锁
WO2018054885A1 (fr) * 2016-09-21 2018-03-29 Knorr-Bremse Systeme für Nutzfahrzeuge GmbH Soupape à seuil de pression destinée à un compresseur à vis pour un véhicule, en particulier un véhicule utilitaire
DE102018104209C5 (de) 2018-02-23 2023-11-30 Hennecke Gmbh Komponentenmischdüse

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN111397894A (zh) * 2020-04-24 2020-07-10 刘勇 一种换挡定压阀污染耐受性能试验系统

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Publication number Publication date
DE20314232U1 (de) 2004-10-21
DE502004000243D1 (de) 2006-04-06
JP2006515661A (ja) 2006-06-01
WO2005021978A1 (fr) 2005-03-10
US20060011875A1 (en) 2006-01-19
EP1540191A1 (fr) 2005-06-15
ATE315729T1 (de) 2006-02-15

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