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
  • F04B19/00—Machines or pumps having pertinent characteristics not provided for in, or of interest apart from, groups F04B1/00 - F04B17/00
  • F04B19/04—Pumps for special use
• • 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
  • 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
  • F04B1/0461—Conical
• • 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
  • F04B19/00—Machines or pumps having pertinent characteristics not provided for in, or of interest apart from, groups F04B1/00 - F04B17/00
  • F04B19/20—Other positive-displacement pumps
  • F04B19/22—Other positive-displacement pumps of reciprocating-piston type
• • 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
  • F04B53/10—Valves; Arrangement of valves
• • 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
  • F04B53/10—Valves; Arrangement of valves
  • F04B53/102—Disc valves
  • F04B53/1022—Disc valves having means for guiding the closure member axially
  • F04B53/1025—Disc valves having means for guiding the closure member axially the guiding means being provided within the valve opening
• • 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
  • F04B53/10—Valves; Arrangement of valves
  • F04B53/1087—Valve seats
• • 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
  • F04B53/10—Valves; Arrangement of valves
  • F04B53/1002—Ball valves
  • F04B53/1007—Ball valves having means for guiding the closure member
• • 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
  • F04B53/10—Valves; Arrangement of valves
  • F04B53/1002—Ball valves
  • F04B53/1017—Semi-spherical ball valves

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 Pump chambers are formed, in each of which a piston that can be moved back and forth 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, the inlet channel being closable by an inlet valve and the outlet channel being closable by an outlet valve, the Inlet valve has a first insert part inserted into the inlet channel and an inlet closing body that can be moved back and forth relative to the first insert part, the first insert part having an inlet valve seat and a guide member arranged offset to 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
• 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 causes them to perform a reciprocating stroke movement. drive.
• 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 inlet valves which each have an insert part and an inlet closing body that can be moved back and forth relative to this insert part.
• the insert part forms an inlet valve seat and a guide member arranged offset in the direction of the associated pump chamber relative to the inlet valve seat.
• 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 adjoins this in the direction of the associated pump chamber and is slidably mounted on the guide member.
• the insert part is usually made of high-grade steel and is pressed into the intake port or held in it in a rotationally fixed and axially non-displaceable manner by flanging. This is associated with not inconsiderable production costs.
• the guide member and the inlet valve stem movably mounted thereon are arranged downstream of the inlet valve seat with respect to the direction of flow of the cleaning liquid. This increases the volume of the pump chamber that cannot be displaced by the piston when it moves in the direction of the intake valve seat, i.e. the so-called dead space. This in turn affects the suction behavior of the piston pump.
• 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 inlet valve seat to be molded directly into a housing part, which also forms a guide member for the inlet closing body, with the guide member being arranged upstream of the inlet valve seat.
• 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 and has improved suction behavior.
• the first insert part consists of a plastic material and has an annular inlet valve seat body that faces the pump chamber and forms the inlet valve seat, with the guide member being arranged upstream of the inlet valve seat in relation to the direction of flow of the cleaning liquid.
• the pump housing of the piston pump according to the invention has two housing parts, each of which is designed as a metal part and therefore has a very high pressure resistance.
• the second housing part forms inlet channels, in each of which a first insert part made of a plastic material is inserted.
• the first insert part has an annular inlet valve seat body which faces the associated pumping chamber and forms the inlet valve seat.
• the first insert part forms a guide member on which the inlet closing body is slidably mounted.
• the first insert 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 made of metal. Since the first insert is made of plastic, its manufacturing costs are relatively low.
• the first insert 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 first insert part assumes a position upstream of the inlet valve seat. This makes it possible to keep the volume that cannot be displaced by the piston, i.e. the so-called dead space, very small.
• the piston pump according to the invention is therefore characterized by relatively low production costs and improved suction behavior.
• 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 second housing part forms an annular first support surface adjoining the inlet channel in the direction of the pumping 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 first support surface of the second housing part.
• the inlet valve seat body preferably has a sealing ring receptacle which is connected to the contact surface and in which the inlet valve seat body opposite the first support surface sealing ring is arranged in the axial direction.
• the sealing ring arranged between the intake valve seat body and the first support surface of the second housing part forms a seal that acts in the axial direction.
• 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 first 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, which is adjoined by a second groove wall, the outer diameter of the inlet valve seat body increasing from the second groove wall as it approaches increased to the contact surface.
• the outer diameter which increases in the direction of the contact surface, reduces the risk that the sealing ring inserted into the sealing ring seat will unintentionally become detached from the sealing ring seat during assembly of the first insert part. In addition, this allows the contact surface to be made relatively large.
• the first groove wall can be designed in the manner of a cone, for example, with the cone angle preferably being about 10° to about 30°, preferably about 15° to about 25°, in particular about 20°. It is advantageous if the outer diameter of the inlet valve seat body increases continuously via the second groove wall with increasing distance from the contact surface.
• the sealing ring receptacle is designed in the manner of a circumferential channel into which a sealing ring can be inserted without the risk of the sealing ring detaching from the sealing ring receptacle when the first insert part is inserted into the inlet channel.
• the first insert part is favorably held in a rotationally fixed and axially non-displaceable manner relative to the inlet channel.
• first insert part can be latched to the second housing part.
• the first insert 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 first insert part has at least one holding arm upstream of the intake valve seat body. With the help of the retaining arm, the first insert part can be easily fixed to the intake port.
• 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 first insert 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 retaining 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 be.
• the at least one holding arm is integrally connected to the inlet valve seat body. In such a configuration, the at least one first retaining arm forms a one-piece plastic molded part together with the inlet valve seat body.
• the first insert 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 first insert part.
• the inlet closing body has an inlet valve stem, which is slidably mounted on a guide member of the first insert 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 first insert 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 removed from the side of the Inlet duct was inserted into the inlet duct.
• 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 retaining arm has been inserted 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 first insert part forms a one-piece plastic molded part in its entirety.
• the first insert part preferably consists of a POM material (polyoxymethylene material).
• the inlet closing body has the inlet valve disk and the 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 first insert part, and the inlet valve stem is slidably mounted on the guide member of the first insert 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 protrudes from the guide member in the direction of the intake line Has shaft portion on which a spring holder is fixed, wherein an intake valve spring is 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 liquid can flow from the suction line via the inlet valve into the pump chamber. 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.
• the second housing part has a valve receptacle into which the outlet channels open
• the piston pump has an outlet valve assembly that forms all the outlet valves
• the outlet valve assembly having a second insert part , which consists of a plastic material and is inserted into the valve seat and which has a plurality of annular outlet valve seat having body, each forming an outlet valve seat.
• the second housing part which is designed as a metal part, has a valve receptacle.
• a second insert part of an outlet valve assembly is inserted into the valve receptacle.
• the second insert part consists of a plastic material and has a plurality of ring-shaped outlet valve seat bodies, each of which forms an outlet valve seat that is in particular aligned with an outlet channel.
• the outlet valve seats are thus provided by the second insert part, so that complex post-processing of the second housing part, which is designed as a metal part, can be dispensed with.
• a single second insert is used, which has all the outlet valve seats of the piston pump according to the invention. This facilitates the assembly of the piston pump.
• 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, which forms all the outlet valves, to be assembled as an independently manageable structural unit even before the complete piston pump is assembled.
• 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 second housing part forms a plurality of annular second 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 with the interposition of a sealing ring applied.
• the vertical orientation of the second support surfaces makes it possible to design the sealing rings that rest against the second support surfaces as axial seals, so that any seals that may arise in the area of the valve receptacle during manufacture of the second housing part and grooves aligned parallel to the longitudinal axis of the valve seat 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 is carried out. 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 second support surfaces, since these are aligned perpendicular to the longitudinal axis of the valve receptacle. Thus, 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 second support surfaces each adjoin an outlet channel in the direction of flow of the cleaning liquid.
• the outlet valves each have an outlet closing body that can be moved back and forth relative to the second insert 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.
• the outlet valve stem is arranged downstream of the outlet valve seat. This results in a further reduction in the dead space of the associated pump chamber and thereby improves the suction behavior of the piston pump.
• 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 body has a plurality of guide elements, each of which guides an outlet valve stem of an outlet closing body. In a preferred embodiment of the invention, 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.
• the outlet valve disk can be pretensioned in the direction of the associated outlet valve seat by means of the outlet valve spring.
• the guide body can be connected to the second insert 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 second insert part in a liquid-tight manner, preferably with the interposition of a sealing ring.
• the second insert 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 plugged into the second insert part.
• the guide body in the second insert can be inserted 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 second insert 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 assume a position immediately downstream of the check valve seat formed by the guide body and can be preloaded by a check valve spring in the direction of the check valve seat.
• the central non-return valve is preferably arranged in the pressure line.
• the first housing part to have 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 second insert is inserted.
• the guide body is connected to the first housing part in a liquid-tight manner and the second insert part is connected to the second housing part in a liquid-tight manner, and moreover the guide body and the second insert part are connected to one another in a liquid-tight manner.
• the pressure line is advantageously connected to the outlet valve assembly. It is favorable if 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 protruding 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 a sealing ring being arranged between the annular projection and 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.
• FIG. 1 a sectional view of a piston pump
• FIG. 2 an enlarged partial illustration of the piston pump from FIG. 1;
• FIG. 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 shows a perspective view of a first insert part of the inlet valve from FIG. 5 before it is installed
• FIG. 8 a sectional view of the first insert part from FIG. 5;
• FIG. 9 a perspective representation of the first insert part of the inlet valve after its assembly
• FIG. 10 a sectional view of the first insert 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.
• 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 .
• Two diametrically opposite recesses 36 , 38 of the second housing part 16 adjoin the inlet channels 32 on the side facing the suction line 20 .
• an annular first support surface 40 adjoins the inlet channels 34 , which is formed by the second housing part 16 and faces the respective pump chamber 24 .
• the first supporting surfaces are oriented perpendicular to the longitudinal axes 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 ports 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 the pressure line 22 connects in the direction of the front side 18 of the first housing part 14.
• 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 a first insert 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 first insertion part 54 .
• the first insert 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 first support surface 40 adjoining the respective inlet channel 32 in the direction of the pump chamber 24 .
• the 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 the inlet valve seat body 60 and a first one directly adjoining the contact surface 64 Has groove wall 70 and a second groove wall 72 adjoining this.
• the outer diameter of the inlet valve seat body 60 decreases continuously via the first groove wall 70 as the distance from the contact surface 64 increases, and the outer diameter of the inlet valve seat body 60 increases continuously via the second groove wall 72 as the distance from the contact surface 64 increases. This is shown in particular in Figures 7 and 9 clear.
• the sealing ring receptacle 66 accommodates a first sealing ring 74 which seals the inlet valve seat body 60 in relation to the first support surface 40 in the axial direction.
• Adjoining the intake valve seat body 60 of the first insert part 54 in the direction of the intake line 20 are two holding arms 76, 78 which are diametrically opposite one another with respect to the longitudinal axis 33 of the intake passage 32, which extend through the intake passage 34 and each have an end section 80, 82 which faces away from the intake valve seat body 60. which projects out of 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 first insert part 54 forms a one-piece plastic molding which defines the intake valve seat body 60 , the retaining 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 is integrally connected to the inlet valve disk 88 on the side of the inlet valve disk 88 facing away from the pump chamber 24 .
• 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. Under the action of the intake valve spring 96, the intake valve disk 88, which is connected in one piece to the intake valve stem 90, is pressed against the intake valve seat 62 of the intake valve seat body 60, so that the intake 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.
• 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.
• first insert part 54 with retaining arms 76, 78 initially aligned in a straight line, as shown in Figures 6 and 7, can be inserted into inlet channel 32 from the side facing pump chamber 24, so that the contact surface 64 comes to rest on the first 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 closing body 56 can then be assembled on the first insert part 54 by inserting the inlet valve stem 90 into the first insert part 54 from the side facing the pump chamber 24 , with 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 pumping 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 exhaust valves 99 are identical configured and are formed by a preassembled 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 a second insert part 102, which consists of a plastic material, for example a POM material.
• the second insert 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 second insert 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 second insert 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 first insert part 54 and 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 sealingly applied to 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.
• Outlet valve spring 120 of an outlet valve 99 is clamped between the guide receptacles 112 and the outlet valve disk 116
• Outlet valve plate 116 is supported and an outlet valve stem 118 surrounds the area between the outlet valve plate 116 and the guide receptacle 112 in the circumferential direction. This becomes particularly clear from FIG.
• An internal groove 122 extending in the longitudinal direction of the guide receptacle 112 is formed in the guide receptacle 112 and through which the cleaning liquid can escape from the guide receptacle 112 .
• the second housing part 16 forms annular second 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 outlet valve seat bodies 114 are each supported with their end faces 126 facing away from the respective outlet valve seat 106 on a second support surface 124, with a second sealing ring 128 being arranged between the end faces 126 and the second support surfaces 124, which seals the respective outlet valve seat body 104 relative to the second housing part 16 sealed in the axial 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 second insert 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 region which dips into the housing recess 46, the guide body 108 forms a check valve seat 140 which faces away from the second insert part 102 and on which a check valve seat 142 can be placed in a sealing manner.
• 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 two housing parts 14 and 16 can each be designed, for example, as a die-cast part or as a formed part.
• they can be made of an aluminum or brass material.
• the provision of the inlet valves 52 and the outlet valves 99 does not require subsequent processing of the metal parts, since the inlet and outlet valves 52, 99 are inserted into the metal parts in the form of plastic components and have the corresponding 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 very small.

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• Engineering & Computer Science (AREA)
• Mechanical Engineering (AREA)
• General Engineering & Computer Science (AREA)
• Details Of Reciprocating Pumps (AREA)

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• 2020
  • 2020-12-01 DE DE102020131796.4A patent/DE102020131796A1/de active Pending
• 2021
  • 2021-09-23 WO PCT/EP2021/076235 patent/WO2022117239A1/de active Application Filing
  • 2021-09-23 EP EP21783435.7A patent/EP4256203A1/de active Pending
  • 2021-09-23 CN CN202180071729.6A patent/CN116490689A/zh active Pending
• 2023
  • 2023-05-31 US US18/326,334 patent/US20230304485A1/en active Pending

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