EP2165767A1 - Hochdruckauslösehebel mit Kraftbetätigungsmechanismus mit doppeltem Übersetzungshebel - Google Patents

Hochdruckauslösehebel mit Kraftbetätigungsmechanismus mit doppeltem Übersetzungshebel Download PDF

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Publication number
EP2165767A1
EP2165767A1 EP08016361A EP08016361A EP2165767A1 EP 2165767 A1 EP2165767 A1 EP 2165767A1 EP 08016361 A EP08016361 A EP 08016361A EP 08016361 A EP08016361 A EP 08016361A EP 2165767 A1 EP2165767 A1 EP 2165767A1
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EP
European Patent Office
Prior art keywords
trigger
primary
link
effective
pivot
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP08016361A
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English (en)
French (fr)
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EP2165767B1 (de
Inventor
Svavar Sigurkarlsson
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.)
Nilfisk AS
Original Assignee
Nilfisk Advance AS
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 Nilfisk Advance AS filed Critical Nilfisk Advance AS
Priority to EP08016361A priority Critical patent/EP2165767B1/de
Priority to AT08016361T priority patent/ATE532584T1/de
Publication of EP2165767A1 publication Critical patent/EP2165767A1/de
Application granted granted Critical
Publication of EP2165767B1 publication Critical patent/EP2165767B1/de
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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B05—SPRAYING OR ATOMISING IN GENERAL; APPLYING FLUENT MATERIALS TO SURFACES, IN GENERAL
    • B05B—SPRAYING APPARATUS; ATOMISING APPARATUS; NOZZLES
    • B05B12/00—Arrangements for controlling delivery; Arrangements for controlling the spray area
    • B05B12/002—Manually-actuated controlling means, e.g. push buttons, levers or triggers
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B05—SPRAYING OR ATOMISING IN GENERAL; APPLYING FLUENT MATERIALS TO SURFACES, IN GENERAL
    • B05B—SPRAYING APPARATUS; ATOMISING APPARATUS; NOZZLES
    • B05B1/00—Nozzles, spray heads or other outlets, with or without auxiliary devices such as valves, heating means
    • B05B1/30—Nozzles, spray heads or other outlets, with or without auxiliary devices such as valves, heating means designed to control volume of flow, e.g. with adjustable passages
    • B05B1/3033—Nozzles, spray heads or other outlets, with or without auxiliary devices such as valves, heating means designed to control volume of flow, e.g. with adjustable passages the control being effected by relative coaxial longitudinal movement of the controlling element and the spray head
    • B05B1/304—Nozzles, spray heads or other outlets, with or without auxiliary devices such as valves, heating means designed to control volume of flow, e.g. with adjustable passages the control being effected by relative coaxial longitudinal movement of the controlling element and the spray head the controlling element being a lift valve
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B08—CLEANING
    • B08B—CLEANING IN GENERAL; PREVENTION OF FOULING IN GENERAL
    • B08B3/00—Cleaning by methods involving the use or presence of liquid or steam
    • B08B3/02—Cleaning by the force of jets or sprays
    • B08B3/026—Cleaning by making use of hand-held spray guns; Fluid preparations therefor
    • B08B3/028—Spray guns
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B05—SPRAYING OR ATOMISING IN GENERAL; APPLYING FLUENT MATERIALS TO SURFACES, IN GENERAL
    • B05B—SPRAYING APPARATUS; ATOMISING APPARATUS; NOZZLES
    • B05B9/00—Spraying apparatus for discharge of liquids or other fluent material, without essentially mixing with gas or vapour
    • B05B9/01—Spray pistols, discharge devices

Definitions

  • the present invention generally relates to a trigger gun for a high-pressure washer, and in particular to the trigger mechanism of such a trigger gun. More specifically, the present invention relates to a trigger mechanism requiring only a small force from the grip of a users hand for opening the valve of a trigger gun.
  • a trigger gun for high-pressure washers generally comprises a handle, a trigger, and a valve.
  • the flow of pressurized liquid is controlled by moving the trigger relative to the handle, which opens or closes the valve by way of a trigger mechanism.
  • the handle In the grip of a user's hand, the handle usually rests against the palm with the thumb oppositely placed from the rest of the fingers, of which some or all rest on the trigger.
  • a certain minimum effort is required to operate the trigger gun. Firstly, the weight of the trigger gun and the components attached to the trigger gun has to be supported against the force of gravity. Secondly, the pushing force from the deployment of the pressurized liquid must be compensated for. Under certain circumstances the force of gravity can be counteracted by the pushing force, e.g. when pointing the trigger gun slightly downwards. Thirdly, a force of action is required for activating the trigger, which can be a tiring exercise when using a trigger gun over an extended period of time.
  • a trigger that amplifies the force of action by way of a simple levering mechanism, where the trigger itself acts as the lever with the fulcrum or pivot point located close to the valve.
  • EP1389495 Another example is disclosed in EP1389495 , which involves a simple levering mechanism with a piston-like pulling mechanism driven by the pressurized liquid upstream from the closing element of the valve. The pulling mechanism provides a helping moment on the levering mechanism, making the trigger be easier and less tiresome to pull,
  • the piston-like pulling mechanism requires a high-precision manufacturing and is vulnerable to impurities in the pressurized liquid.
  • An object according to the present invention is to provide trigger gun for a high-pressure washer, where the trigger gun has a robust trigger mechanism that requires only a small force on the trigger to operate its valve.
  • a particular feature of the present invention is that it provides a stronger amplification of the force applied to the trigger when opening a closed valve, than when opening an open valve even further.
  • the trigger mechanism may amplify the force in the grip formed between the thumb and the index, or the thumb and the long finger, the most, which allows a more balanced and ergonomic handling of the trigger gun. The force required of a users grip for activating the trigger gun, as well as the force required for continuously operating the trigger gun, may be reduced.
  • an advantage with the present invention is that the operating of the trigger requires a smaller effort.
  • a trigger gun for a high-pressure washer comprises a handle, a valve rigidly supported by the handle, a trigger having a first area or point of contact for manually applying a force, and a trigger mechanism.
  • the valve further comprises an actuation element for the opening and closing the valve, and the trigger mechanism provides a cooperation between the trigger and the actuation element for enabling a manual control of the opening and closing of the valve.
  • the trigger gun further comprises a rocker arm having a second area or point of contact for cooperation with the actuation element, a primary elbow link, and a secondary elbow link.
  • the trigger mechanism further comprises a primary mechanical linkage constituted by the handle, trigger, primary elbow link, and rocker arm that are pivotally connected in a closed loop, and a secondary mechanical linkage constituted by the handle, trigger, secondary elbow link, and rocker arm that also are pivotally connected in a closed loop.
  • the valve has a closed state, a first open state and a second open state, whereby the primary mechanical linkage is employed when changing the valve from its closed state to its first open state, and the secondary mechanical linkage is employed when changing the valve from its first open state to its second open state.
  • An advantage according to the first aspect of the present invention is that the five links of the trigger mechanism, i.e. the handle, trigger, primary elbow link, secondary elbow link, and rocker arm, do not require high-precision machining.
  • a mechanical link of this kind can be made robust, without the use of high strength materials. This allows for the use of cheaper to manufacture and lighter trigger mechanisms. Further, the large number of possible geometric and spatial configurations of four-link mechanical linkages allows for an ergonomically optimized trigger gun, being both light weight and comfortable to handle.
  • the primary trigger mechanism may convert a force of action applied at the first area or point of contact to an amplified primary force of reaction at the second area or point of contact acting on the actuation element.
  • the secondary trigger mechanism may convert a force of action applied at the first area or point of contact to an amplified secondary force of reaction at the second area or point of contact acting on the actuation element.
  • Trigger guns for high-pressure washers commonly have valves with a valve seat between an upstream valve passage and a downstream valve passage.
  • a valve body located in the downstream valve passage seal against the valve seat.
  • the liquid under pressure only reaches the downstream valve passage, where the pressure generates a pressure force on the valve body.
  • the valve body has to be lifted against this pressure force.
  • the pressurized liquid also defines the pressure in the downstream valve passage, which will counteract the earlier pressure force.
  • a greater force is required to open this kind of valve from a closed state, than to from an already open state.
  • the handle may be connected to the trigger by a first joint or pivot, the trigger to the primary elbow link by a primary second joint or pivot, the trigger to the secondary elbow link by a secondary second joint or pivot, the primary elbow link to the rocker arm by a primary third joint or pivot, the secondary elbow link to the rocker arm by a secondary third joint or pivot, the rocker arm to the handle by a fourth joint or pivot.
  • the second area or point of contact may then be located closer to the fourth joint or pivot than to any of the first, primary second, secondary second, primary third, and secondary third joints or pivots. This will allow the mechanical linkage to provide a high ratio of the force of reaction over the force of action, as this ratio increases with a decreased distance to the fourth joint or pivot. However, the distance over which the force of reaction can act decreases with a decreased distance to the fourth joint or pivot. Hence, a certain distance between the second area or point of contact and the fourth joint or pivot is required for the trigger mechanism to work.
  • the primary mechanical linkage may further constitute a first slot or guideway located on the trigger or the primary elbow link. This first slot or guideway disengage and guide the primary second joint or pivot when employing the trigger mechanism for changing the valve from its first open state to its second open state.
  • the secondary mechanical linkage may further constitute a second slot or guideway located on the trigger or the secondary elbow link. This second slot or guideway disengage and guide the secondary second joint or pivot when employing the trigger mechanism for changing the valve from its closed state to its first open state.
  • the primary mechanical linkage may further constitute a third slot or guideway located on the primary elbow link or the rocker arm.
  • This third slot or guideway disengage and guide the primary third joint or pivot when employing the trigger mechanism for changing the valve from its first open state to its second open state.
  • the secondary mechanical linkage may further constitute a fourth slot or guideway located on the secondary elbow link or the rocker arm. This fourth slot or guideway disengage and guide the secondary third joint or pivot when employing the trigger mechanism for changing the valve from its closed state to its first open state.
  • the slots or guideways described here enable a robust trigger mechanism with a single trigger being a link In two different mechanical linkages operating in sequence after one another when the trigger Is pulled. It may be an advantage to have the slots or guideways In connection with the primary and secondary second joints or pivots only, as it allows for a more compact construction of the trigger gun, since when disconnected the elbow links then may slide inside the trigger or the handle.
  • the trigger mechanism may comprise more than two elbow links, where each elbow link is coupled to the trigger and/or the rocker arm by one or more slots or guideways accordingly.
  • the trigger mechanism may enable more than two different amplification levels of the force of action.
  • the primary mechanical linkage gives a stronger amplification than the subsequent secondary mechanical linkage, which in turn gives a smaller amplification than the subsequent tertiary mechanical linkage.
  • An advantage of having an additional tertiary mechanical linkage of this kind is that, when operating the trigger gun with the trigger fully pressed, less effort is required due to stronger amplification.
  • the smaller amplification of the secondary mechanical linkage may be needed for opening the valve a certain length, allowing larger flows of the pressurized.
  • a line between the fourth joint or pivot and the first joint or pivot define an effective handle link
  • a line between the first joint or pivot and the primary second joint or pivot define a primary effective trigger link
  • a line between the primary second joint or pivot and the primary third joint or pivot define a primary effective elbow link
  • a line between the primary third joint or pivot and the fourth joint or pivot define a primary effective rocker link
  • a line between the first joint or pivot and the secondary second joint or pivot define a secondary effective trigger link
  • a line between the secondary second joint or pivot and the secondary third joint or pivot define a secondary effective elbow link
  • a line between the secondary third joint or pivot and the fourth joint or pivot define a secondary effective rocker link.
  • the primary effective elbow link and/or the secondary effective elbow link may be shorter than any of the effective handle link, primary effective trigger link, primary effective rocker link, secondary effective trigger link, and secondary effective rocker link.
  • the effective trigger link inside the grip of the user's hand, this particular feature allows for a more compact construction and a slimmer handle of the trigger gun.
  • the second area or point of contact it is not necessary for the second area or point of contact to be located on the effective rocker link; it only has to move in a pivotal motion defined by the rocker arm and the effective rocker link.
  • the primary effective elbow link may be longer than the secondary effective rocker link. This may be an advantage, as it also allows for a compact construction and a larger amplification of the primary force of reaction.
  • the primary effective trigger link and the primary effective elbow link jointly define a primary effective trigger angle; the secondary effective trigger link and the secondary effective elbow link jointly define a secondary effective trigger angle.
  • the primary and secondary effective trigger angles may be obtuse and increase when pulling the trigger for opening the valve. With a trigger constructed for being pulled towards the palm of a user's hand, these constraints on the angles may give a ratio of the primary force of reaction over the force of action and a ratio of the secondary force of reaction over the force of action that increase with the pulling of the trigger, which in Itself may be an advantage.
  • the obtuse and increasing primary and secondary effective trigger angles may be favourable where the valve is located in front of the gripping hand, as it allows for a compact design by bringing the primary and secondary effective trigger links closer to the effective handle link.
  • the primary and/or secondary effective trigger angles may be acute.
  • the primary and/or secondary effective elbow angles may be obtuse.
  • the joints of each of the primary and secondary mechanical linkages may define a complex, convex, or concave quadrilateral.
  • the handle may be constructed for being received in the palm of a user's hand so that the primary second joint or pivot and/or the secondary second joint or pivot are located closer to the index finger than the little finger of the user's hand.
  • this relative positioning of the index finger and the third joint or pivot means that the index and long fingers performs the longest pulling motion when activating the trigger, as the effective trigger link performs a pivotal motion around the first joint or pivot. This is an advantage, since the index and long fingers are longer and contributes more to the strength of a grip than the index and little finger.
  • the handle may be constructed for being received in the palm of a user's hand so that the trigger moves relative to the users palm when employing the trigger for opening the valve. Further, the handle may be constructed for being received in the palm of a user's hand so that a finger of the users hand is inside the closed loops of the primary and secondary mechanical linkages. Clearly, this will allow a more compact and less cumbersome construction of the trigger gun.
  • Fig. 2c outlines the effective mechanical linkages of the trigger gun illustrated in Fig. 1c with the valve in its second open position.
  • FIG. 1a A cross-sectional view of a presently preferred embodiment of trigger gun 1 for a high-pressure washer Is shown in Fig. 1a .
  • the handle 2 of the trigger gun 1 rigidly supports a valve 3 for controlling and limiting the flow of pressurized liquid from a high-pressure washer.
  • the pressurized liquid usually having a pressure in the range 100-8000 bar, is led from the high-pressure washer to the trigger gun 1 by a hose, which is connected to the trigger gun 1 at the inlet connection 26.
  • the liquid flows from the inlet connection 26 through the valve 3 to the outlet connection 27, to which a hollow lance, wand or a similar tubular device can be coupled for employing the pressurized liquid at a distance from the trigger gun 1.
  • the valve 3 has an actuation element 6 extending outside the valve house for controlling the valve 3.
  • the valve 3 is opened by pressing the actuation element 6 towards the valve body.
  • the valve 3 has the property that the actuation element 6 presents a greater resistance when opening the valve 3 from a closed state than from an already open state. This means that the needed force of reaction applied to the actuation element 6 is smaller for maintaining an open valve 3, or for opening the valve 3 further when already being open, than for opening the valve 3 when it is closed.
  • the trigger gun comprises a trigger mechanism having a primary mechanical linkage constituted by a handle 2, a trigger 4, a primary elbow link 37 and a rocker arm 8, which are connected in a closed loop, and a secondary mechanical linkage constituted by the same handle 2, trigger 4, and rocker arm 8, but with a different secondary elbow link 38 in another closed loop.
  • Each of the mechanical linkages is connected by four joints, of which two, 10 and 13, are employed in both of the mechanical linkages, while two primary joints 11-12 complete the primary mechanical linkage, and the two secondary joints 39-40 complete the secondary mechanical linkage.
  • the trigger 4 has a first area or point of contact 5, e.g. corresponding to the location at which the long finger of a user is placed when operating the trigger gun.
  • the rocker arm has a second area or point of contact 9 for cooperating with the actuation element 6 by conveying a force component being parallel to the direction of movement of the actuation element 6.
  • the mechanical linkage can convert a force of action applied to the first area or point of contact 5 to a force of reaction at the second area or point of contact 9.
  • one or more of the joints 10-13 and 39-40 may be a pivot or a contraption with a similar function, where the joints pivotally connecting the links also may move relative to one another.
  • Fig. 1a the trigger 4 is not pulled, i.e. the trigger mechanism is not engaged and the valve 3 is in Its closed state.
  • a second slot 47 allows the secondary second joint 39 to move relative to the trigger 4, which means that the secondary mechanical linkage is unengaged, and that the primary force of reaction applied to the actuation element 6 is defined by the primary mechanical linkage.
  • the same presently preferred embodiment of a trigger gun 1 as in Fig. 1 a is illustrated in Fig. 1b , but with trigger pulled so that that the secondary second joint 39 has reached the end of the second slot 47, thereby engaging the secondary mechanical linkage. Simultaneously the first mechanical linkage is disengaged by letting the primary second joint slide in the first slot 46.
  • valve has reached Its first open position and the secondary force of reaction applied to the actuation element 6 is now defined by the secondary mechanical linkage.
  • the valve has reached its second open position and the primary second joint 11 has reached the end of the first slot 46, which hinders the functional movement of the secondary mechanical linkage.
  • Figs.2a-c depict the effective links of the mechanical linkages in Figs.1a-c , respectively, with solid lines corresponding to engaged mechanical linkages and dashed lines corresponding to unengaged mechanical linkages.
  • the location of the first 10, primary second 11, primary third 12, and fourth 13 joints define the primary effective mechanical linkage constituted by the effective handle link 14, primary effective trigger link 15, primary effective elbow link 16, and primary effective rocker link 17 connecting the joints 10-13 in a closed loop.
  • the primary effective trigger link 15 and the primary effective elbow link 16 jointly define a primary effective trigger angle 29, while the primary effective elbow link 16 and the primary effective rocker link 17 jointly define a primary effective elbow angle 18.
  • the location of the first 10, secondary second 39, secondary third 40, and fourth 13 joints define the secondary effective mechanical linkage constituted by the effective handle link 14, secondary effective trigger link 41, secondary effective elbow link 42, and secondary effective rocker link 43 connecting the joints 10, 13 and 39-40 in a closed loop.
  • the secondary effective trigger link 41 and the secondary effective elbow link 42 jointly define a secondary effective trigger angle 44, while the secondary effective elbow link 42 and the secondary effective rocker link 43 jointly define a secondary effective elbow angle 45.
  • the length of the primary effective elbow link 16 Is longer than its secondary counterpart 42, while the primary effective trigger link 15 is shorter than its secondary counterpart 41.
  • the primary 29 and secondary 44 effective trigger angles are obtuse, while both of the primary 18 and secondary 45 effective elbow angles are acute. These four angles all increase when pulling the trigger, i.e. when the primary 15 and secondary 41 effective trigger links perform a pivotal motion indicated by the first arrow 30.
  • Fig. 2a corresponds to an engaged primary mechanical linkage at the start of the pulling of the trigger with an unengaged secondary mechanical linkage.
  • a force of action applied to the trigger is represented by the first arrow 30 being perpendicular to the primary effective trigger link 15.
  • the primary mechanical linkage converts the force of action to a primary force of reaction, which is represented by the second arrow 31 being perpendicular to the primary effective rocker link 17.
  • the mechanical advantage obtained i.e. the ratio of the absolute primary force of reaction over the absolute force of action, or the length of the second arrow 31 over the length of the first arrow 30, is greater than one, corresponding to an amplification of the applied force.
  • Fig. 2b corresponds to the situation where the primary mechanical linkage Is disengaged, while the secondary mechanical linkage is simultaneously engaged.
  • the force of action having the an unchanged magnitude, is represented by the first arrow 30 having, which has the same length and acting at the same distance from the first joint 10 as previously, but from direction being perpendicular to the secondary effective trigger link 41 instead. Due to the length of and the angles between the secondary effective links 41-43, the mechanical advantage is now smaller than for the primary mechanical linkage, resulting in a smaller secondary force of reaction. This is represented by a shorter second arrow 31, which is now perpendicular to the secondary effective rocker link 43, but connecting at the same distance from the fourth link 13 as in the earlier situation.
  • Fig. 2c corresponds to the situation where the trigger is fully pulled, i.e. the primary mechanical linkage is still disengaged while the secondary effective angles 44-45 have increased to their maximum broadness. At this point the mechanical advantage of the secondary mechanical linkage has reached its maximum, which is represented by a longer second arrow 31 than in Fig. 2b .
  • the lengths of the arrows in Figs.2a-c are only to show the qualitative, and not the actual quantitative, relationship between the force of action and the primary and secondary force of reaction.
  • the first arrow 30 acts from a direction such that the mechanical advantage will increase when the primary 15 and secondary 41 effective trigger links 15 move in the direction indicated by the first arrow 30. If the direction of the first arrow 30 were to be reversed, the direction of the second arrow 31 would be the opposite and the mechanical advantage would decrease when the trigger link 15 moves in the reverse direction.
  • the mechanical advantage is defined as the ratio of the length of the second arrow 31 over the length of the first arrow 30, or the absolute value of the force of reaction over the absolute value of the force of action, it can be defined as the ratio of the distances travelled by the point of contact of the first arrow 30 over the distance simultaneously travelled by point of contact of the second arrow 31 when the trigger is pulled.
  • this definition is only relevant for small pulling motions.
  • 'primary', 'secondary', 'tertiary', etc. is not to reflect any direct rank or order, but primarily to distinguish between elements and components having similar form or function. However, an effort has been made to make 'primary' rejecting components or functions primarily employed at the beginning of the pulling the trigger, and 'secondary' reflecting components or functions primarily employed at the end of the pulling of the trigger.

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  • Portable Nailing Machines And Staplers (AREA)
EP08016361A 2008-09-17 2008-09-17 Hochdruckauslösehebel mit Kraftbetätigungsmechanismus mit doppeltem Übersetzungshebel Active EP2165767B1 (de)

Priority Applications (2)

Application Number Priority Date Filing Date Title
EP08016361A EP2165767B1 (de) 2008-09-17 2008-09-17 Hochdruckauslösehebel mit Kraftbetätigungsmechanismus mit doppeltem Übersetzungshebel
AT08016361T ATE532584T1 (de) 2008-09-17 2008-09-17 Hochdruckauslösehebel mit kraftbetätigungsmechanismus mit doppeltem übersetzungshebel

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP08016361A EP2165767B1 (de) 2008-09-17 2008-09-17 Hochdruckauslösehebel mit Kraftbetätigungsmechanismus mit doppeltem Übersetzungshebel

Publications (2)

Publication Number Publication Date
EP2165767A1 true EP2165767A1 (de) 2010-03-24
EP2165767B1 EP2165767B1 (de) 2011-11-09

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EP08016361A Active EP2165767B1 (de) 2008-09-17 2008-09-17 Hochdruckauslösehebel mit Kraftbetätigungsmechanismus mit doppeltem Übersetzungshebel

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EP (1) EP2165767B1 (de)
AT (1) ATE532584T1 (de)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2015086085A1 (de) * 2013-12-12 2015-06-18 Alfred Kärcher Gmbh & Co. Kg Ventilpistole für ein hochdruckreinigungsgerät
US20160279655A1 (en) * 2013-12-12 2016-09-29 Alfred Kärcher Gmbh & Co. Kg Valve gun for a high-pressure cleaner
WO2017162282A1 (de) * 2016-03-23 2017-09-28 Alfred Kärcher Gmbh & Co. Kg Ventilpistole für ein hochdruckreinigungsgerät

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2107686A (en) * 1935-09-27 1938-02-08 Binks Mfg Co Spray gun for spraying fabrics
DE690762C (de) * 1937-12-23 1940-05-06 Leipziger Tangier Werk Akt Ges Spritzpistole
GB826699A (en) * 1956-02-25 1960-01-20 Waldemar Foerstner Improvements in or relating to regulators for nozzles
US5284301A (en) * 1992-12-15 1994-02-08 Wagner Spray Tech Corporation Double-pivot trigger
DE19614663A1 (de) 1996-04-13 1997-10-16 Suttner Gmbh & Co Kg Ventilpistole, insbesondere für ein Hochdruckreinigungsgerät
EP1389495A1 (de) 2001-11-30 2004-02-18 Alfred Kärcher GmbH & Co. KG Schliessvorrichtung für die Flüssigkeitsabgabeleitung eines Hochdruckreinigungsgerätes
EP1516674A2 (de) * 2003-09-16 2005-03-23 ALTO Deutschland GmbH HD-Pistole mit Rückstellung der Drosselventil-Funktion

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2107686A (en) * 1935-09-27 1938-02-08 Binks Mfg Co Spray gun for spraying fabrics
DE690762C (de) * 1937-12-23 1940-05-06 Leipziger Tangier Werk Akt Ges Spritzpistole
GB826699A (en) * 1956-02-25 1960-01-20 Waldemar Foerstner Improvements in or relating to regulators for nozzles
US5284301A (en) * 1992-12-15 1994-02-08 Wagner Spray Tech Corporation Double-pivot trigger
DE19614663A1 (de) 1996-04-13 1997-10-16 Suttner Gmbh & Co Kg Ventilpistole, insbesondere für ein Hochdruckreinigungsgerät
EP1389495A1 (de) 2001-11-30 2004-02-18 Alfred Kärcher GmbH & Co. KG Schliessvorrichtung für die Flüssigkeitsabgabeleitung eines Hochdruckreinigungsgerätes
EP1516674A2 (de) * 2003-09-16 2005-03-23 ALTO Deutschland GmbH HD-Pistole mit Rückstellung der Drosselventil-Funktion

Cited By (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2015086085A1 (de) * 2013-12-12 2015-06-18 Alfred Kärcher Gmbh & Co. Kg Ventilpistole für ein hochdruckreinigungsgerät
CN105813763A (zh) * 2013-12-12 2016-07-27 阿尔弗雷德·凯驰两合公司 用于高压清洁设备的阀枪
US20160279655A1 (en) * 2013-12-12 2016-09-29 Alfred Kärcher Gmbh & Co. Kg Valve gun for a high-pressure cleaner
US20160288148A1 (en) * 2013-12-12 2016-10-06 Alfred Kärcher Gmbh & Co. Kg Valve gun for a high-pressure cleaner
CN106232241A (zh) * 2013-12-12 2016-12-14 阿尔弗雷德·凯驰两合公司 用于高压清洁设备的阀枪
US9993832B2 (en) 2013-12-12 2018-06-12 Alfred Kärcher Gmbh & Co. Kg Valve gun for a high-pressure cleaner
CN105813763B (zh) * 2013-12-12 2018-11-13 阿尔弗雷德·凯驰两合公司 用于高压清洁设备的阀枪
CN106232241B (zh) * 2013-12-12 2018-12-28 阿尔弗雷德·卡赫欧洲两合公司 用于高压清洁设备的阀枪
EP3450025A1 (de) * 2013-12-12 2019-03-06 Alfred Kärcher SE & Co. KG Ventilpistole für ein hochdruckreinigungsgerät
WO2017162282A1 (de) * 2016-03-23 2017-09-28 Alfred Kärcher Gmbh & Co. Kg Ventilpistole für ein hochdruckreinigungsgerät

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EP2165767B1 (de) 2011-11-09
ATE532584T1 (de) 2011-11-15

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