EP4256202A1 - Pompe à piston pour dispositif de nettoyage haute pression - Google Patents

Pompe à piston pour dispositif de nettoyage haute pression

Info

Publication number
EP4256202A1
EP4256202A1 EP21782730.2A EP21782730A EP4256202A1 EP 4256202 A1 EP4256202 A1 EP 4256202A1 EP 21782730 A EP21782730 A EP 21782730A EP 4256202 A1 EP4256202 A1 EP 4256202A1
Authority
EP
European Patent Office
Prior art keywords
inlet
outlet
piston pump
valve seat
pump according
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.)
Pending
Application number
EP21782730.2A
Other languages
German (de)
English (en)
Inventor
Robert Nathan
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.)
Alfred Kaercher SE and Co KG
Original Assignee
Alfred Kaercher SE 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 Alfred Kaercher SE and Co KG filed Critical Alfred Kaercher SE and Co KG
Publication of EP4256202A1 publication Critical patent/EP4256202A1/fr
Pending legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/04—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
    • F04B1/0404—Details or component parts
    • F04B1/0452—Distribution members, e.g. valves
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/04—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
    • F04B1/0404—Details or component parts
    • F04B1/0421—Cylinders
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
    • F04B53/007—Cylinder heads
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
    • F04B53/16—Casings; Cylinders; Cylinder liners or heads; Fluid connections
    • F04B53/162—Adaptations of cylinders
    • F04B53/164—Stoffing boxes

Definitions

  • the invention relates to a piston pump for a high-pressure cleaning device for delivering a cleaning liquid, having a pump housing which has a first housing part and a second housing part, each of which is designed as a metal part, the first housing part forming a suction line and a pressure line, and the second housing part forming a plurality of forms pump chambers, in each of which a reciprocating piston is immersed and which are each in flow communication with the suction line via an inlet channel and with the pressure line via an outlet channel, with the inlet channels each being closable by an inlet valve and the outlet channels each by an outlet valve, wherein the outlet valves each have a stationary outlet valve seat and an outlet closing body that can be moved back and forth relative to the outlet valve seat and has an outlet valve disk that can be placed sealingly against the outlet valve seat.
  • Such piston pumps are known from DE 10 2009 049 095 A1.
  • a cleaning liquid supplied via the suction line for example water
  • a pressure hose can be connected to the pressure line, for example, which carries a nozzle head at its free end, via which the pressurized cleaning liquid can be directed onto an object.
  • the piston pump is driven by a drive motor, which is coupled to the pistons of the piston pump via a swash plate mechanism, for example, and drives them to perform a reciprocating stroke movement.
  • the pump housing has a first and a second housing part, each of which is designed as a metal part.
  • the first housing part forms the suction line and the pressure line
  • the second housing part forms the pump chambers and the inlet and outlet channels, via which the pump chambers are in flow connection with the suction line and the pressure line.
  • the inlet channels can each be closed by an inlet valve and the outlet channels can each be closed by an outlet valve.
  • DE 10 2009 049 095 A1 proposes outlet valves that each have an outlet part and an outlet closing body that can be moved back and forth relative to it.
  • the outlet part forms an outlet valve seat and the outlet closing body has an outlet valve plate which can be placed against the outlet valve seat in a sealing manner.
  • Each outlet part is held stationary in an outlet channel.
  • the outlet part is usually made of high-grade steel and is pressed into an outlet channel or held in it in a rotationally fixed and axially non-displaceable manner by flanging.
  • Piston pumps for high-pressure cleaning devices are known from WO 2008/086950 A1 and EP 2 805 050 B1, in which the two housing parts of the pump housing are made of a plastic material. This allows the outlet valve seats to be molded directly into a housing part without requiring an additional outlet part.
  • pump housings made of a plastic material have a lower compressive strength than pump housings made of metal parts.
  • the object of the present invention is to further develop a piston pump of the type mentioned at the outset in such a way that it can be produced more cost-effectively.
  • this object is achieved according to the invention in that the second housing part has a valve receptacle into which all the outlet channels open, and that the piston pump has an outlet valve assembly that forms all the outlet valves, the outlet valve assembly having an outlet part that consists of a plastic material and is inserted into the valve seat and that forms all the outlet valve seats.
  • the piston pump according to the invention has an outlet valve assembly that forms all the outlet valves.
  • the outlet valve assembly includes an outlet portion that is seated in a valve seat.
  • the valve receptacle is formed by the second housing part, which is designed as a metal part.
  • the outlet part is made of a plastic material and has all the outlet valve seats.
  • the outlet valve seats of the piston pump are thus provided by the outlet part. It is therefore not necessary to set a separate outlet part, which forms an outlet valve seat, in an outlet channel for each outlet valve.
  • Complex post-processing of the second housing part, which is designed as a metal part can also be omitted.
  • a single outlet part is used, which has all the outlet valve seats of the piston pump according to the invention and is made of a plastic material. This reduces the manufacturing costs of the piston pump and facilitates its assembly.
  • the first housing part and/or the second housing part is preferably designed as a die-cast part or as a formed part.
  • the first housing part and/or the second housing part is/are preferably made from an aluminum or brass material.
  • the valve receptacle is preferably arranged on that side of the second housing part which faces the first housing part.
  • the outlet valve assembly is advantageously designed as a pre-assembled unit. This allows the outlet valve assembly to be assembled as a self-contained assembly, even before assembly of the complete piston pump.
  • the outlet valve assembly can be assembled at a first assembly location and then shipped to a second assembly location where assembly of the complete piston pump occurs.
  • the outlet part preferably has a plurality of annular outlet valve seat bodies, each of which forms an outlet valve seat.
  • the outlet valve seat is preferably aligned with an outlet channel.
  • the second housing part forms a plurality of annular outlet support surfaces in the area of the valve receptacle, which are aligned perpendicularly to a longitudinal axis of the valve receptacle and each connect to an outlet channel in the direction of flow of the cleaning liquid and on each of which an outlet valve seat body rests with the interposition of a sealing ring .
  • the vertical orientation of the outlet support surfaces makes it possible to design the sealing rings that are in contact with the outlet support surfaces as axial seals, so that any scores that may occur during manufacture of the second housing part in the area of the valve receptacle and are aligned parallel to the longitudinal axis of the valve receptacle do not impair the sealing effect of the sealing rings.
  • Such grooves can arise in particular when the second housing part is designed as a die-cast part, during the production of which demolding takes place.
  • Any grooves that occur in the area of the valve receptacle during demolding extend in the direction of demolding, i.e. they extend parallel to the longitudinal axis of the valve receptacle, but not parallel to the outlet support surfaces, since these are aligned perpendicular to the longitudinal axis of the valve receptacle.
  • any grooves that occur when the second housing part is demoulded in the area of the valve receptacle cannot impair the seal acting in the axial direction.
  • the outlet support surfaces preferably each adjoin an outlet channel in the direction of flow of the cleaning liquid.
  • the outlet valve assembly forms all the outlet valves of the piston pump. It is favorable if the outlet valves each have an outlet closing body that can be moved back and forth relative to the outlet part, which has an outlet valve disk that can be placed sealingly against an outlet valve seat and an outlet valve stem that adjoins the outlet valve disk in the direction away from the outlet channel. In relation to the direction of flow of the cleaning liquid, the outlet valve stem is arranged downstream of the outlet valve seat.
  • the outlet valve assembly preferably has a guide body which consists of a plastic material and has a plurality of guide elements, on each of which an outlet valve stem is mounted in a displaceable manner. In such a configuration, all outlet valve shafts are guided by means of the guide body. This further simplifies the assembly of the piston pump.
  • the guide elements are set up to each guide an outlet valve stem of an outlet closing body.
  • the guide elements each form a guide receptacle into which an outlet valve stem dips.
  • the guide receptacles each have at least one inner groove extending in the longitudinal direction of the guide receptacle. Cleaning fluid can escape from the respective guide mount via the inner groove.
  • An outlet valve spring is advantageously clamped in each case between the guide elements and the outlet valve disk. Using the exhaust valve spring the outlet valve plate can be biased in the direction of the associated outlet valve seat.
  • the guide body can be connected to the outlet part in a detachable and liquid-tight manner.
  • the outlet valve stems can each be inserted into a guide receptacle of the guide body, with the outlet valve stems being surrounded by an outlet valve spring in their area protruding from the guide receptacles, which is supported on a guide receptacle on the one hand and on an outlet valve plate on the other.
  • the guide body can then be connected to the outlet part in a liquid-tight manner, preferably with the interposition of a sealing ring.
  • the outlet part connected to the guide body can be inserted into the valve receptacle of the second housing part. Then the two housing parts of the pump housing can then be joined together.
  • the guide body can preferably be connected to the outlet part in a plug-in manner with the interposition of one or more sealing rings.
  • the guide body can be inserted into the outlet part with the interposition of at least one sealing ring.
  • the guide body forms a check valve seat for a central check valve arranged downstream of the outlet valves.
  • the outlet part forms the valve seats of the outlet valves and the guide body forms the valve seat of the central check valve. This further simplifies the assembly of the piston pump.
  • a check valve closing body can and can assume a position directly downstream of the check valve seat formed by the guide body be biased towards the check valve seat by a check valve spring.
  • the central non-return valve is preferably arranged in the pressure line.
  • the first housing part to have, on its side facing the second housing part, a housing recess which is aligned with the valve receptacle of the second housing part and into which the guide body dips with the interposition of at least one sealing ring.
  • the outlet valve assembly assumes a position between the first housing part and the second housing part, with the first housing part having a housing recess on its side facing the second housing part, into which the guide body dips, and with the second housing part on its first housing part side facing has a flush with the housing recess aligned valve receptacle, in which the outlet part is inserted.
  • the guide body is connected to the first housing part in a liquid-tight manner and the outlet part is connected to the second housing part in a liquid-tight manner, and the guide body and the outlet part are also connected to one another in a liquid-tight manner.
  • the pressure line is advantageously connected to the outlet valve assembly.
  • the at least one sealing ring which is arranged between the guide body and the housing recess of the first housing part, surrounds the guide body in the circumferential direction.
  • the guide body has an outwardly projecting annular projection, to which a step of the housing recess directed radially inward relative to the longitudinal axis of the housing recess is assigned, with between the annular projection and a sealing ring is arranged on the step.
  • the sealing ring can form an axial seal, so that scores that may occur during manufacture of the first housing part in the area of the housing recess and are aligned parallel to the longitudinal axis of the housing recess do not impair the sealing effect of the sealing ring.
  • Such grooves can arise in particular when the first housing part is designed as a die-cast part, during the manufacture of which demolding is carried out.
  • any grooves that occur during demoulding in the area of the housing recess extend in the direction of demolding, ie they extend parallel to the longitudinal axis of the housing recess, but not parallel to the radially inward step. Thus, any grooves that occur when the first housing part is demoulded in the area of the housing recess cannot impair the seal acting in the axial direction.
  • the inlet valves each have an inlet part inserted into an inlet channel and an inlet closing body that can be moved back and forth relative to the inlet part, the inlet part having an inlet valve seat and a guide member arranged offset from the inlet valve seat and wherein the inlet closing body has an inlet valve disk that can be placed sealingly against the inlet valve seat and an inlet valve stem that is connected to the inlet valve disk and is slidably mounted on the guide member, the inlet part being made of a plastic material and having an annular inlet valve seat body that faces the pump chamber and forms the inlet valve seat , and wherein the guide member is arranged upstream of the inlet valve seat with respect to the flow direction of the cleaning liquid is.
  • the second housing part forms inlet channels, in each of which an inlet part made of a plastic material is inserted.
  • the inlet member includes an annular inlet valve seat body facing the associated pumping chamber and forms the intake valve seat. Relative to the flow direction of the cleaning liquid upstream of the inlet valve seat body, ie offset in the direction of the suction line to the inlet valve seat body, the inlet part forms a guide member on which the inlet closing body is slidably mounted.
  • the inlet part made of plastic allows an inlet valve seat to be provided in a cost-effective manner without the need for complex post-processing of the second housing part. Since the inlet part is made of plastic, its manufacturing costs are relatively low.
  • the inlet part can be inserted into the inlet channel from the side of the inlet channel facing the associated pump chamber, so that the guide member formed by the inlet part assumes a position upstream of the inlet valve seat and thus outside the pump chamber. This makes it possible to keep the volume of the pump chamber that cannot be displaced by the piston during a movement in the direction of the inlet valve, i.e. the so-called dead space, small. This improves the suction behavior of the piston pump.
  • the second housing part forms an annular inlet support surface adjoining the inlet channel in the direction of the pump chamber, which is aligned perpendicular to the longitudinal axis of the inlet channel and on which the inlet valve seat body rests with a contact surface.
  • the inlet valve seat body is supported by the inlet support surface of the second housing part.
  • the inlet valve seat body preferably has a sealing ring receptacle adjoining the contact surface, in which a sealing ring sealing the inlet valve seat body relative to the inlet support surface in the axial direction is arranged.
  • a sealing ring sealing the inlet valve seat body relative to the inlet support surface in the axial direction is arranged.
  • the sealing ring arranged between the inlet valve seat body and the inlet support surface of the second housing part forms a seal that acts in the axial direction out.
  • Such grooves can arise in particular when the second housing part is designed as a die-cast part, during the production of which demolding is carried out. Any grooves that occur during demoulding extend in the direction of demolding, ie they extend parallel to the longitudinal axis of the inlet channel, but not parallel to the inlet support surface, since this is aligned perpendicular to the longitudinal axis of the inlet channel. This means that scoring, which occurs when the second housing part is demoulded, cannot impair the seal that acts in the axial direction.
  • the sealing ring seat forms an annular groove surrounding the inlet valve seat body in the circumferential direction with a first groove wall adjoining the contact surface, via which the outer diameter of the inlet valve seat body decreases continuously with increasing distance from the contact surface and which is adjoined by a second groove wall .
  • the sealing ring receptacle is preferably designed in the manner of a circumferential channel into which a sealing ring can be inserted. This reduces the risk of the sealing ring unintentionally detaching from the sealing ring seat when the inlet part is inserted into the inlet channel.
  • the first groove wall can, for example, be designed in the manner of a cone, with the cone angle preferably being approximately 10° to 30°, preferably approximately 15° to 25°, in particular 20°.
  • the outer diameter of the inlet valve seat body increases continuously via the second groove wall with increasing distance from the contact surface.
  • the inlet part is favorably held in a rotationally fixed and axially non-displaceable manner relative to the inlet channel.
  • the inlet part can be latched to the second housing part.
  • the inlet part has at least one holding arm, which adjoins the inlet valve seat body in the direction of the intake line and is held in a rotationally fixed manner relative to the inlet port.
  • the inlet part has at least one holding arm upstream of the inlet valve seat body. The inlet part can be easily fixed to the inlet port with the aid of the retaining arm. The at least one holding arm dips into the inlet channel.
  • the at least one holding arm preferably reaches through the inlet channel.
  • the at least one holding arm engages behind the inlet channel on its side facing the suction line. This can ensure that the inlet part, after it has been inserted so far into the inlet channel from the side facing the associated pumping chamber that the at least one holding arm engages behind the inlet channel on the side facing away from the pumping chamber, can then no longer be easily removed from the inlet channel can.
  • the at least one holding arm is integrally connected to the inlet valve seat body.
  • the at least one first retaining arm forms a one-piece plastic molded part together with the inlet valve seat body.
  • the inlet part preferably has two holding arms lying diametrically opposite one another with respect to the longitudinal axis of the inlet channel.
  • the two holding arms allow a mirror-symmetrical and thus highly resilient design of the inlet part.
  • the inlet closing body has an inlet valve stem, which is slidably mounted on a guide member of the inlet part. It is advantageous if the guide member is fixed to the at least one holding arm.
  • the guide member is preferably bonded to the at least one holding arm.
  • the guide member forms a one-piece plastic molded part together with the at least one retaining arm and preferably together with the inlet valve seat body.
  • the at least one retaining arm has an end section which faces away from the inlet valve seat body and which dips into a recess in the second housing part.
  • the end section of the at least one holding arm forms a form fit with the recess of the second housing part. This makes it possible in a simple manner to fix the inlet part in a rotationally fixed manner on the second housing part.
  • the end section of the at least one holding arm can be thermally deformed. This makes it possible to reshape the at least one holding arm in a simple manner by applying heat after it has been inserted into the inlet channel from the side of the inlet channel facing the associated pump chamber.
  • the at least one holding arm can consist of a thermally deformable plastic material.
  • the at least one retaining arm can, for example, be configured in a straight line before being inserted into the intake port and can be thermally deformed into a curved or angled shape after being inserted into the intake port.
  • the end section of the at least one retaining arm facing away from the intake valve seat body is thermally deformed radially outwards after the insertion of the retaining arm into the intake port, so that after the thermal deformation the end section is directed outwards in relation to the longitudinal axis of the intake port and the Inlet channel engages behind on the side facing away from the pump chamber.
  • the inlet part forms a one-piece plastic molded part in its entirety.
  • the inlet part preferably consists of a POM material (polyoxymethylene material).
  • the inlet closing body has an inlet valve disk and an inlet valve stem adjoining the inlet valve disk on its side facing away from the pump chamber.
  • the inlet valve disk can be placed sealingly against the inlet valve seat of the inlet part, and the inlet valve stem is slidably mounted on the guide member of the inlet part.
  • the inlet valve disk is preferably connected to the inlet valve stem in a materially bonded manner.
  • the guide member is preferably designed in the shape of a ring.
  • the inlet valve stem extends through the guide member and has a stem section protruding from the guide member in the direction of the intake line, on which a spring holder is fixed, with an inlet valve spring being clamped between the spring holder and the guide member.
  • the inlet valve spring which is supported on the one hand on the spring holder and on the other hand on the guide member, the inlet valve stem and with it the inlet valve disk can be subjected to a spring force, under the effect of which the inlet valve disk is pressed against the inlet valve seat.
  • the inlet valve plate can lift off the inlet valve seat against the action of the inlet valve spring, so that cleaning fluid can flow out of the Suction line can flow into the pump chamber via the inlet valve. If the piston executes a pressure movement in the opposite direction, the inlet valve disk is pressed against the inlet valve seat by the inlet valve spring, so that the cleaning liquid cannot flow back into the suction line via the inlet valve.
  • the guide member forms a stop that limits the movement of the inlet valve stem in the direction of the pump chamber and thus also the movement of the inlet valve disk in the direction of the pump chamber.
  • FIG. 1 a sectional view of a piston pump
  • FIG. 2 an enlarged partial illustration of the piston pump from FIG. 1;
  • Figure 3 is an enlarged sectional view of Detail X of Figure 2 showing an outlet valve assembly of the piston pump;
  • FIG. 4 a perspective representation of a second housing part of the piston pump
  • FIG. 5 an enlarged sectional view of detail Y from FIG. 2, showing an inlet valve of the piston pump;
  • FIG. 6 a sectional view of the intake valve from FIG. 5 along the line 6-6;
  • FIG. 7 a perspective illustration of an inlet part of the inlet valve from FIG. 5 before it is installed;
  • FIG. 8 a sectional view of the inlet part from FIG. 5;
  • FIG. 9 a perspective representation of the inlet part of the inlet valve after its assembly
  • FIG. 10 a sectional view of the inlet part from FIG. 9;
  • Figure 11 a sectional view of the outlet valve assembly from Figure 3.
  • FIG. 10 an advantageous embodiment of a piston pump according to the invention for a high-pressure cleaning device is shown schematically and assigned the reference numeral 10 overall.
  • a cleaning liquid preferably water
  • the piston pump 10 includes a pump housing 12 with a first housing part 14 and a second housing part 16.
  • the two housing parts 14, 16 are each designed as a metal part. In the embodiment shown, they are each designed in the form of an aluminum die-cast part.
  • the first housing part 14 defines the front side 18 of the piston pump 10 and forms a suction line 20 and a pressure line 22 .
  • the second housing part 16 forms three pump chambers, in each of which a piston dips. To achieve a better overview, only one pump chamber 24 and two pistons 26, 28 are shown in the drawing. All the pistons are inserted in an oscillating manner into the respective pump chamber 24 by a known swash plate, not shown in the drawing, and by a den respective piston surrounding coil spring 30 pushed back out of the pump chamber, so that the volume of the pump chambers 24 changes periodically.
  • Each pump chamber 24 is in fluid communication with the suction line 20 via an inlet channel 32 of the second housing part 16 .
  • Each pump chamber 24 is flow-connected to the pressure line 22 via an outlet channel 34 of the second housing part 16 .
  • the inlet channels 32 are aligned parallel to one another and each have a longitudinal axis 33 .
  • Cleaning liquid to be pressurized can be sucked into the respective pump chamber 24 via the inlet channels 32 , and the cleaning liquid can be discharged from the pump chambers 24 via the outlet channels 34 .
  • the outlet channels 34 open into a central valve receptacle 42 of the second housing part 16, which is delimited by a cylinder wall 44 in the circumferential direction.
  • the valve receptacle 42 is arranged on the side of the second housing part 16 facing the first housing part 14 and has a longitudinal axis 43 which is aligned parallel to the longitudinal axes 33 of the inlet channels 32 .
  • the first housing part 14 On its side facing the second housing part 16, the first housing part 14 has a housing recess 46 which is aligned with the valve receptacle 42 of the second housing part 16 and to which in Direction of the front side 18 of the first housing part 14, the pressure line 22 connects.
  • a bypass line 48 branches off from the housing recess 46, which is formed by the first housing part 14 and in which a bypass valve 50, which is known per se and is therefore shown only schematically in the drawing, is arranged.
  • the bypass line 48 establishes a flow connection between the housing recess 46 and the suction line 20 and can be closed by means of the bypass valve 50 .
  • the inlet channels 32 can each be closed by an inlet valve 52 .
  • the inlet valves 52 are configured identically and each have an inlet part 54 which consists of a plastic material, preferably a POM material, and which is inserted into an inlet channel 32 .
  • the inlet valves 52 each have an inlet closing body 56 which can be moved back and forth in the axial direction relative to the inlet part 54 .
  • the inlet part 54 has an inlet valve seat body 60 which forms an inlet valve seat 62 of the respective inlet valve 52 .
  • the inlet valve seat body 60 protrudes into the associated pump chamber 24 and is supported with a contact surface 64 facing away from the respective pump chamber 24 on the inlet support surface 40 adjoining the respective inlet channel 32 in the direction of the pump chamber 24 .
  • Contact surface 64 is adjoined by a sealing ring receptacle 66 in the form of an annular groove 68, which extends over the circumference of inlet valve seat body 60 and has a first groove wall 70 directly adjoining contact surface 64 and a second groove wall 72 adjoining this.
  • the outer diameter of the intake valve seat body 60 decreases continuously via the first groove wall 70 as the distance from the contact surface 64 increases.
  • the outer diameter of the intake valve seat body 60 increases continuously via the second groove wall 72 as the distance from the contact surface 64 increases. This is particularly clear from FIGS .
  • the sealing ring receptacle 66 accommodates a first sealing ring 74 which seals the inlet valve seat body 60 against the inlet support surface 40 in the axial direction.
  • Adjoining the intake valve seat body 60 of the intake part 54 in the direction of the intake line 20 are two retaining arms 76, 78 which are diametrically opposite one another with respect to the longitudinal axis 33 of the intake port 32, which extend through the intake port 34 and each have an end section 80, 82 which faces away from the intake valve seat body 60 protrudes from the inlet channel 32 on the side of the inlet channel 32 facing away from the pump chamber 24 and, when the inlet valve 52 is in the installed state, engages behind the respective inlet channel 32 by immersing itself in a recess 36, 38 in the second housing part 16 and forming a form fit with it. This is explained in more detail below.
  • the retaining arms 76, 78 receive an annular guide member 84 between them.
  • the outer diameter of the guide member 84 is smaller than the diameter of the inlet channel 32. This allows the cleaning liquid to flow around the guide member 84 within the inlet channel 32.
  • the guide member 84 is integrally connected to the retaining arms 76, 78, and the retaining arms 76, 78 are integrally connected to the intake valve seat body 60.
  • the inlet portion 54 forms a one-piece plastic molding that defines the inlet valve seat body 60, the support arms 76, 78 and the guide member 84.
  • the inlet closing body 56 has an inlet valve disk 88 and an inlet valve stem 90 , which faces away from the pump chamber 24 Side of the intake valve plate 88 integrally connects to this.
  • the intake valve disk 88 can be placed sealingly against the intake valve seat 62 of the intake valve seat body 60, and the intake valve stem 90 extends through the guide member 84 in the direction of the intake line 20.
  • a spring retainer 94 is fixed on a shaft section 92 of the intake valve shaft 90 that projects out of the guide member 84 in the direction of the intake line 20 .
  • An intake valve spring 96 is clamped between the spring retainer 94 and the guide member 84 .
  • Inlet valve spring 96 is designed as a helical spring, which is supported on one side on spring holder 94 and on the other side on guide member 84 and surrounds inlet valve stem 90 in the area between guide member 84 and spring holder 94 in the circumferential direction.
  • the inlet valve disk 88 which is connected in one piece to the inlet valve stem 90, is pressed against the inlet valve seat 62 of the inlet valve seat body 60, so that the inlet valve 52 assumes its closed position.
  • the inlet valve 52 opens, in that the inlet valve disk 88 is lifted off the inlet valve seat 62 against the spring force of the inlet valve spring 96, thereby establishing a flow connection from the suction line 20 to the Pump chamber 24 releases, so that cleaning liquid can flow from the suction line 20 via the inlet channel 32 into the pump chamber 24.
  • the cleaning liquid can flow around the spring retainer 94, the inlet valve spring 96 and the guide member 84 on the outside, so that flow losses can be kept low.
  • the intake valve plate 88 can be lifted off the intake valve seat 62 until the spring retainer 94 comes into contact with a stop 98 of the guide member 84 designed in the manner of a projection or a sleeve.
  • the stop 98 thus limits the lifting movement of the intake valve disk 96. If the piston 26, 28 moves in the direction of the inlet channel 32, the inlet valve disk 88 assumes its position on the inlet valve seat, so that the cleaning liquid cannot flow back into the suction line 20 again.
  • the inlet part 54 with the retaining arms 76, 78 initially aligned in a straight line, as shown in Figures 6 and 7, can be inserted into the inlet channel 32 from the side facing the pump chamber 24, so that the Contact surface 64 comes to rest on the inlet support surface 40 and the end sections 80 , 82 of the retaining arms 76 , 78 protrude from the inlet duct 32 on the side of the inlet duct 32 facing away from the pump chamber 24 .
  • the end sections 80, 82 can then be thermally formed, with the end sections 80, 82 being pressed radially outwards and entering the recesses 36, 38 and forming a form fit with them.
  • the inlet part 54 is held on the inlet channel 32 in an axially immovable and non-rotatable manner.
  • the inlet closing body 56 can then be assembled on the inlet part 54 by inserting the inlet valve stem 90 into the inlet part 54 from the side facing the pump chamber 24 , the inlet valve stem 90 reaching through the guide member 84 .
  • the inlet valve spring 96 can then be placed on the shaft section 92 protruding from the guide member 84 on the side facing away from the pump chamber 24 , and then the spring holder 94 can be fixed to the shaft section 92 .
  • the fixing of the spring holder 94 on the shaft section 92 can take place, for example, by means of ultrasonic welding.
  • the outlet channels 34 opening into the valve receptacle can each be closed by an outlet valve 99 .
  • the outlet valves 99 are designed identically and are formed by a preassemblable outlet valve assembly 100 which is received by the valve receptacle 42 of the second housing part 16 and the housing recess 46 of the first housing part 14 .
  • the outlet valve assembly 100 is shown in Figures 3 and 11 enlarged. It includes an outlet part 102, which consists of a plastic material, for example a POM material.
  • the outlet part 102 is inserted into the valve receptacle 52 and has a plurality of annular outlet valve seat bodies 104 which each form an outlet valve seat 106 of an outlet valve 99 .
  • the outlet valve assembly 100 has a guide body 108, which also consists of a plastic material, for example a fiber-reinforced plastic material, and which can be connected to the outlet part 102 in a detachable and liquid-tight manner.
  • the guide body 108 forms guide elements 110 in the form of guide receptacles 112 which are each aligned in alignment with an outlet valve seat 106 .
  • the outlet part 102 and the guide body 108 accommodate between them a plurality of outlet closing bodies 114 which can be moved back and forth relative to the outlet part 54 and to the guide body 108 and each have an outlet valve disk 116 and an outlet valve stem 118 of an outlet valve 99 which is integrally connected thereto.
  • the outlet valve disk 116 can be placed sealingly against an outlet valve seat 106, and the outlet valve stem 118 adjoining it on the side of the outlet valve disk 116 facing away from the outlet valve seat 106 dips into a guide receptacle 112 in which it is displaceably mounted.
  • An outlet valve spring 120 of an outlet valve 99 is clamped between the guide receptacles 112 and the outlet valve disk 116, which is supported on one side on a guide receptacle 112 and on the other side on an outlet valve disk 116 and surrounds an outlet valve stem 118 in the area between the outlet valve disk 116 and the guide receptacle 112 in the circumferential direction.
  • An inner groove 122 that extends in the longitudinal direction of the guide receptacle 112 and via which the cleaning liquid can escape from the guide receptacle 112 .
  • the second housing part 16 forms annular outlet support surfaces 124 , which each adjoin an outlet channel 34 in the direction of the valve receptacle 42 and are aligned perpendicularly to the longitudinal axis 43 of the valve receptacle 42 .
  • the end faces 126 of outlet valve seat bodies 114 facing away from the respective outlet valve seat 106 are each supported on an outlet support surface 124, with a second sealing ring 128 being arranged between the end faces 126 and the outlet support surfaces 124, which seals the respective outlet valve seat body 104 axially relative to the second housing part 16 direction.
  • the guide body 108 is surrounded in the circumferential direction by an annular groove 130 in which a third sealing ring 132 is arranged.
  • the third sealing ring 132 ensures the liquid-tight connection between the outlet part 102 and the guide body 108 .
  • the housing recess 46 forms a step 136 directed radially inwards.
  • a fourth sealing ring 138 is positioned between the annular projection 134 and the step 136, which seals the guide body 108 in the axial direction with respect to the first housing part 14.
  • the guide body 108 In its area which dips into the housing recess 46, the guide body 108 forms a non-return valve seat 140 which is remote from the outlet part 102 and on which a non-return closing body 142 can be placed in a sealing manner. In combination with the non-return closing body 142 , the non-return valve seat 140 forms a central non-return valve 144 .
  • the outlet valve assembly 100 is designed as a preassemblable structural unit and can be inserted into the valve receptacle 42 and the housing recess 46 when the piston pump 10 is assembled. Since the outlet valve assembly 100 forms all of the outlet valves 99, this simplifies the assembly of the piston pump 10.
  • the two housing parts 14 and 16 are designed as metal parts.
  • the provision of the inlet valves 52 and the outlet valves 99 does not require any subsequent processing of the metal parts, since the inlet parts 54 and the outlet part 102 are inserted into the metal parts in the form of plastic components and provide the valve seats.
  • the piston pump 10 can therefore be produced inexpensively.
  • piston pump 10 is characterized by good suction behavior, since the volume of the pump chambers 24 that cannot be displaced by the pistons 26, 28 of the piston pump 10 can be kept small.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Details Of Reciprocating Pumps (AREA)
  • Electrical Discharge Machining, Electrochemical Machining, And Combined Machining (AREA)
  • Cleaning By Liquid Or Steam (AREA)
  • Valve Housings (AREA)
  • Lift Valve (AREA)

Abstract

L'invention concerne une pompe à piston (10) pour un dispositif de nettoyage haute pression, comprenant un corps de pompe (12) qui présente une première partie de corps (14) et une seconde partie de corps (16), chacune d'elles étant réalisée sous la forme d'une pièce métallique. La première partie de corps (14) forme une conduite d'aspiration (20) et une conduite de refoulement (22), et la seconde partie de corps (16) forme de multiples chambres de pompe (24), dans chacune desquelles un piston (26, 28) peut être déplacé en va-et-vient et dont chacune est reliée fluidiquement à la conduite d'aspiration (20) par l'intermédiaire d'un canal d'admission (32) et à la conduite de refoulement (22) par l'intermédiaire d'un canal de refoulement (34). Le canal d'admission (32) peut être fermé par une soupape d'admission (52), et le canal de refoulement (34) peut être fermé par une soupape de refoulement (99). Chacune des soupapes de refoulement (99) présente un siège de soupape de refoulement (106) qui est maintenu fixe et un corps de fermeture de soupape de refoulement (114) qui peut être déplacé en va-et-vient par rapport au siège de soupape de refoulement et qui comporte un disque de soupape de refoulement (116) qui peut être placé de manière étanche contre un siège de soupape de refoulement (106). Afin de perfectionner la pompe à piston (10) de sorte qu'elle puisse être produite de manière peu coûteuse, la seconde partie de corps (16) présente une zone de réception de soupape (42), dans laquelle tous les canaux de refoulement (34) s'ouvrent, et la pompe à piston (10) comporte un ensemble de soupapes de refoulement (100) qui forme toutes les soupapes de refoulement (99), l'ensemble de soupapes de refoulement (100) présentant une partie de refoulement (102) qui est constituée d'une matière plastique et qui est insérée dans la zone de réception de soupape (42) et qui forme tous les sièges de soupape de refoulement (106).
EP21782730.2A 2020-12-01 2021-09-23 Pompe à piston pour dispositif de nettoyage haute pression Pending EP4256202A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102020131798.0A DE102020131798A1 (de) 2020-12-01 2020-12-01 Kolbenpumpe für ein hochdruckreinigungsgerät
PCT/EP2021/076241 WO2022117240A1 (fr) 2020-12-01 2021-09-23 Pompe à piston pour dispositif de nettoyage haute pression

Publications (1)

Publication Number Publication Date
EP4256202A1 true EP4256202A1 (fr) 2023-10-11

Family

ID=77998992

Family Applications (1)

Application Number Title Priority Date Filing Date
EP21782730.2A Pending EP4256202A1 (fr) 2020-12-01 2021-09-23 Pompe à piston pour dispositif de nettoyage haute pression

Country Status (8)

Country Link
US (1) US20230304480A1 (fr)
EP (1) EP4256202A1 (fr)
JP (1) JP2023550903A (fr)
CN (1) CN116368297A (fr)
AU (1) AU2021390658A1 (fr)
DE (1) DE102020131798A1 (fr)
MX (1) MX2023006441A (fr)
WO (1) WO2022117240A1 (fr)

Family Cites Families (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR1344108A (fr) 1963-01-18 1963-11-22 Compresseur à débit variable
DE6948188U (de) 1969-12-07 1970-04-16 Appbau Gauting Gmbh Axialkolben-luftverdichter
GB1307866A (en) 1970-07-04 1973-02-21 Mitchell Co John E Compressor unit
WO2004074683A1 (fr) 2003-02-21 2004-09-02 Zexel Valeo Climate Control Corporation Compresseur volumetrique a pistons
DE102005050009B4 (de) 2005-10-11 2007-07-05 Alfred Kärcher Gmbh & Co. Kg Hochdruckreinigungsgerät
DE102007003521B4 (de) 2007-01-18 2011-06-09 Alfred Kärcher Gmbh & Co. Kg Kolbenpumpe für ein Hochdruckreinigungsgerät
DE102009049095A1 (de) 2009-10-01 2011-04-07 Alfred Kärcher Gmbh & Co. Kg Pumpe für ein Hochdruckreinigungsgerät
EP2805055B1 (fr) 2012-01-20 2016-05-25 Alfred Kärcher GmbH & Co. KG Pompe à piston pour un appareil de nettoyage sous haute pression
WO2013107520A1 (fr) 2012-01-20 2013-07-25 Alfred Kärcher Gmbh & Co. Kg Pompe à pistons pour appareil de nettoyage à haute pression
WO2013123969A1 (fr) * 2012-02-20 2013-08-29 Alfred Kärcher Gmbh & Co. Kg Pompe pour nettoyeur haute pression et nettoyeur haute pression

Also Published As

Publication number Publication date
US20230304480A1 (en) 2023-09-28
MX2023006441A (es) 2023-06-15
JP2023550903A (ja) 2023-12-06
CN116368297A (zh) 2023-06-30
AU2021390658A1 (en) 2023-06-29
DE102020131798A1 (de) 2022-06-02
WO2022117240A1 (fr) 2022-06-09
AU2021390658A9 (en) 2024-05-02

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