CN104053907A - Piston pump for a high-pressure cleaning device - Google Patents
Piston pump for a high-pressure cleaning device Download PDFInfo
- Publication number
- CN104053907A CN104053907A CN201280067559.5A CN201280067559A CN104053907A CN 104053907 A CN104053907 A CN 104053907A CN 201280067559 A CN201280067559 A CN 201280067559A CN 104053907 A CN104053907 A CN 104053907A
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- CN
- China
- Prior art keywords
- suction valve
- pump
- pressure
- valve seat
- valve
- 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.)
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Classifications
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- 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
- F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
- F04B1/14—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis having stationary cylinders
- F04B1/18—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis having stationary cylinders having self-acting distribution members, i.e. actuated by working fluid
- F04B1/182—Check valves
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- 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
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- 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
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- 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
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Details Of Reciprocating Pumps (AREA)
Abstract
The invention relates to a piston pump (10) for a high-pressure cleaning device having a plurality of pump chambers (20), into which in each case one piston (22) which can move to and fro dips and which are flow-connected in each case via an upstroke valve (24) to a suction inlet (14) and via a delivery valve (26) to a pressure outlet (16), wherein the upstroke valve (24) comprises an upstroke-valve closing body (28) which can bear sealingly against an upstroke-valve seat (30), and wherein the delivery valve (26) comprises a delivery-valve closing body (48) which can bear sealingly against a delivery-valve seat (52), wherein the delivery-valve seat (52) and the upstroke-valve seat (30) are at different radial spacings from a pump longitudinal axis (64). In order to develop the piston pump in such way that it has an increased mechanical load-bearing capability without the material thickness thereof being increased, it is proposed that the delivery-valve seat (52) is arranged offset with respect to the upstroke-valve seat (30) in the circumferential direction of the piston pump in relation to the pump longitudinal axis (64).
Description
Technical field
The present invention relates to a kind of reciprocating pump for high-pressure cleaning appliance, this reciprocating pump has multiple pump chambers, can reciprocating piston insert respectively in these pump chambers, and these pump chambers respectively by suction valve be pumped into that interruption-forming is mobile to be connected
and form to flow by pressure valve and pressure export and be connected, wherein, suction valve comprises suction valve closed shape, this suction valve closed shape can abut on suction valve seat hermetically, and wherein, pressure valve comprises pressure valve closed shape, this pressure valve closed shape can abut on pressure valve seat hermetically, wherein, pressure valve seat radially staggers and arranges about pump longitudinal axis relative jam valve seat.
Background technique
Such reciprocating pump is disclosed by WO 2008/086950A1.By this reciprocating pump, can make liquid, particularly water, be placed under pressure and for example alignment surface or object, so that clean this surface or object.Reciprocating pump has multiple pump chambers, and piston inserts respectively in these pump chambers.Piston is moved reciprocatingly by driving.This causes the volume of pump chamber can periodic variation, and liquid can be inhaled in pump chamber and in pump chamber and be placed under pressure via suction valve by suction ingress thus, and is and then output via pressure valve and pressure export.On suction entrance, can connect for example supply lines, and on pressure export, can connect for example pression hose, this pression hose for example, at its free end place carrying output mechanism, nozzle or spray gun.
Reciprocating pump suffers huge mechanical load at its run duration, and this is because reciprocating pump must bear the fluid pressure that is greater than 100 bar (bar).Therefore, the housing of reciprocating pump has very large material thickness conventionally.This is specially adapted to aspirate the region between valve seat and pressure valve seat, and this is because pump case load especially consumingly in this region.
Summary of the invention
Task of the present invention is, improves and starts the reciprocating pump of mentioning type as follows, that is, make reciprocating pump in the situation that need not improving its material thickness, have the load capacity of raising.
For such reciprocating pump, this task solves as follows according to the present invention, that is, pressure valve seat about pump longitudinal axis week of reciprocating pump upwards relative jam valve seat stagger and arrange.
Each pump chamber of reciprocating pump is furnished with suction valve seat and pressure valve seat.Conventionally, the location of the core of suction valve seat and pressure valve seat is in the common cross section of reciprocating pump, and wherein, this cross section comprises pump longitudinal axis.Different from such layout, in reciprocating pump according to the present invention, pressure valve seat about pump longitudinal axis week of reciprocating pump upwards relative jam valve seat stagger and arrange.Show, by the layout staggering of pressure valve seat, reciprocating pump has the mechanical load ability having improved, and needn't improve the material thickness of reciprocating pump for this reason.Therefore,, in the case of the material thickness remaining unchanged, the liquid that transport can be placed under higher pressure.
Advantageously, pressure valve seat staggers and arranges with the angle of 10 ° to 40 ° about pump longitudinal axis relative jam valve seat.The particularly angle in the region between 20 ° to 30 °, for example angle of 25 °, is proved to be favourable, to improve the mechanical load ability of reciprocating pump without raising material thickness in the situation that.
About pump longitudinal axis, pressure valve seat is arranged on identical height with suction valve seat in an advantageous manner in the axial direction.
Advantageously, suction valve seat and pressure valve seat are made up of plastic materials.
In favourable mode of execution, reciprocating pump has three suction valve seats of arranging evenly distributedly around piston longitudinal axis and three pressure valve seats of arranging evenly distributedly around piston longitudinal axis.In this design proposal, suction valve seat is arranged with the angular separation of 120 ° to each other, and pressure valve seat also has the angular separation of 120 ° relative to each other.Therefore, not only aspirate valve seat but also pressure valve seat and all form the corner point of imaginary equilateral triangle.At this, the suction imaginary leg-of-mutton central point of valve seat and the imaginary leg-of-mutton central point of pressure valve seat overlap.But the imaginary triangle of the imaginary triangle relative jam valve seat of pressure valve seat reverses and arranges around piston longitudinal axis.Advantageously 10 ° to 40 ° of corners, particularly 20 ° to 30 °, preferably 25 °.
In particularly preferred design proposal, reciprocating pump according to the present invention comprises the pump housing and pump head, and wherein, pump head has suction entrance and pressure export, and the pump housing comprises pump chamber and holds suction valve and pressure valve, and wherein, pump head is placed on the edge triangular in shape of the pump housing, wherein, in the plan view of the pump housing, suction valve is arranged in the corner region at edge, and in the plan view of the pump housing, pressure valve is surrounded by cylinder shape inner wall in inside, edge.Such design gives reciprocating pump extra high mechanical load ability, and the material thickness of oversize piston pump significantly for this reason.
Suction valve has respectively suction valve passage and suction valve closing spring, and this suction valve passage can be sealed by suction valve closed shape, and this suction valve closing spring loads suction valve closed shape with spring force in the direction towards suction valve passage.At this advantageously, suction valve closing spring has the mode of axial spacing to locate with relative jam valve passage.In such design proposal, the liquid flowing in pump chamber can flow through on suction valve closing spring side, and this suction valve closing spring needn't be forcibly by liquid percolation.This has reduced the flow loss in suction valve closing spring region
this is because keeping very littlely for the flow loss being produced by suction valve closing spring.
Preferably, suction valve closing spring is arranged in suction valve chamber, and this suction valve chamber forms to flow by suction valve passage and pump chamber and is connected, wherein, keeping arm has the mode of spacing to stretch in suction valve chamber with relative jam valve passage, and suction valve closing spring is supported on this keeping arm.In known reciprocating pump, suction valve closing spring is directly supported on suction valve passage, and the necessary percolation suction valve closing spring of liquid, to arrive suction valve passage.This is optional in improvement project of the present invention, this be because suction valve closing spring with its end portion supports towards suction valve passage on keeping arm, this keeping arm with relative jam valve passage have the mode of spacing stretch into suction valve chamber in.
Advantageously, keeping arm is radially orientated about piston longitudinal axis.
Suction valve chamber is only partly kept arm and runs through in favourable mode of execution of the present invention, that is to say, keeping arm freely protrudes from the wall of suction valve chamber, and without get at its free end suction valve chamber in diametrically opposite wall region.
For example can specify, keeping arm only approximately stretches into the middle part of suction valve chamber.
Advantageously, keeping arm constructs the guide portion for suction valve closed shape.Thus, can prevent that suction valve closed shape from tilting when the to-and-fro motion in simple mode.
Keeping arm comprises break-through opening in an advantageous manner, and this break-through opening is run through by suction valve closed shape.
Suction valve closed shape can for example be designed to mushroom-like and comprise valve disc, on this valve disc, is connected with valve rod, and wherein, this valve rod runs through the break-through opening of keeping arm and guided by keeping arm.
Particularly advantageously, suction valve closing spring tensioning between keeping arm and suction valve closed shape in the side that deviates from suction valve passage of keeping arm.In such structure, suction valve closing spring one side is supported in the side that deviates from suction valve passage of keeping arm, and opposite side is supported on suction valve closed shape.To this, suction valve closed shape can have spring retainer.Advantageously, the bar pressing of spring retainer and suction valve closed shape.
Brief description of the drawings
Following description of the preferred embodiment of the present invention is by reference to the accompanying drawings for further elaboration.Wherein:
Fig. 1 illustrates the schematic longitudinal section according to the preferred implementation of reciprocating pump of the present invention;
Fig. 2 illustrates the plan view of the pump housing of the reciprocating pump in Fig. 1;
Fig. 3 illustrates along the sectional view of the pump housing of the line 3-3 in Fig. 2;
Fig. 4 illustrates along the sectional view of the suction valve of the line 4-4 in Fig. 3; And
Fig. 5 illustrates along the sectional view of the pump housing of the line 5-5 in Fig. 2.
Embodiment
Schematically illustrated according to the preferred implementation of reciprocating pump of the present invention in the accompanying drawings, it marks with reference character 10 on the whole.This reciprocating pump comprises the pump head 12 with suction entrance 14 and pressure export 16.On suction entrance 14, can connect supply lines, carry the liquid that will be placed under pressure can to reciprocating pump 10 by this supply lines.On pressure export 16, can connect outlet line, the liquid being placed under pressure can be aimed to object or surface by this outlet line, so that cleaning objects or surface by reciprocating pump 10.Outlet line can carry output mechanism on its free end, for example spray gun or nozzle.
Pump head is placed on the pump housing, and this pump housing comprises the pump chamber of three same configuration altogether, and piston inserts respectively in these pump chambers.At one of them pump chamber 20 shown in Fig. 1, Fig. 3, Fig. 4 and Fig. 5, piston 22 stretches in this pump chamber.Each pump chamber 20 is attached troops to a unit suction valve 24 and pressure valve 26.By suction valve 24, liquid can be sucked in pump chamber 20 by suction entrance 14, and by pressure valve 26, the liquid being placed in pump chamber 20 under pressure can release from pump chamber 20.
Suction valve 24 comprises respectively suction valve closed shape 28, and this suction valve closed shape can abut on suction valve seat 30 hermetically.Suction valve seat 30 surrounds suction valve passage 32.By suction valve passage 34, pump chamber 20 forms to flow with suction valve chamber 34 and is connected, and this suction valve chamber is formed in the pump housing 18 in the side that faces pump head 12 of the pump housing 18.Keeping arm 36 has the mode of axial spacing to stretch in suction valve chamber 34 with relative jam valve passage 32, and this keeping arm extends approximately to the middle part of aspirating valve chamber 34, and this keeping arm has break-through opening 38 in the mode being orientated alignedly with suction valve passage 32.
Suction valve closed shape 28 is designed to mushroom-like.It comprises the valve disc 40 stretching in pump chamber 20, is integrally connected with valve rod 42 on this valve disc, and this valve rod runs through suction valve passage 32 and inserts in suction valve chamber 34.Valve rod 42 run through the break-through opening 38 of keeping arm 36 and on its free end bearing spring retainer 44, this spring retainer is press fit on valve rod 42.Suction valve closing spring 46 tensioning between spring retainer 44 and keeping arm 36.Suction valve closing spring 46 is configured to helical spring, and surrounds valve rod 42 in region between keeping arm 36 and spring retainer 44.Under the effect of suction valve closing spring 46, the valve disc 40 of suction valve closed shape 28 is forced on suction valve seat 30.
Pressure valve 26 has pressure valve closed shape 48, and this pressure valve closed shape is pressed onto on pressure valve seat 52 by pressure valve closing spring 50.Pressure valve 26 is arranged in valve pressure chamber 54.Each pump chamber 20 of reciprocating pump 20 is attached troops to a unit suction valve chamber 34 and valve pressure chamber 54, and wherein, all valve pressure chambers 54 of reciprocating pump 10 are all transitioned in common central compartment 56, and this central compartment is made up of the pump housing 18 and pump head 12.In central compartment 56, be inserted with central inserting member 58, this central authorities' inserting member is surrounded by seal ring and has centre gangway 60, and this centre gangway can be sealed by central closed shape 62.Closed shape 62 constructs central safety check in conjunction with central inserting member, and pressure line 66 is connected on this central authorities' safety check in the mode being orientated coaxially with pump longitudinal axis 64, and central compartment 56 forms mobile connection by this pressure line with pressure export 16.
The element that is placed with energy resiliently deformable in centre, pump head 12 is in axial direction arranged on the pump housing 18.In illustrated embodiment, the element design of energy resiliently deformable is seal ring 68.Seal ring 68 surrounds the edge 70 of the flange-shape of the pump housing 18.This is particularly clearly shown that in Fig. 2.Rim 70 has the shape with the equilateral triangle of the corner region of rounding.Referring to the plan view of the pump housing 18, suction valve 24 is arranged in the corner region at edge 70.This is particularly clearly shown that in Fig. 2.Edge 70 surrounds columniform inwall 72, and this inwall limits central compartment 56 in the pump housing 18 regions.In the plan view of the pump housing 18, pressure valve 26 is arranged in inwall 72 inside.This is also clearly shown that in Fig. 2.
As already mentioned, each pump chamber 20 is attached troops to a unit has with aspirating the suction valve 24 of valve seat 30 and the pressure valve 26 with pressure valve seat 52.As clear illustrating like that in Fig. 2 particularly, corresponding pressure valve seat 52 is about pump longitudinal axis 64, not only reciprocating pump 10 in the radial direction and also its week upwards with aspirate valve seat 30 and staggering and arrange.Pressure valve seat 52 and the radial spacing of pump longitudinal axis 64 are less than the radial spacing of suction valve seat 30 and pump longitudinal axis 64, and week of reciprocating pump 10 upwards, pressure valve seat 52 relative jam valve seat 30 in illustrated embodiment staggers with the angle α of about 25 °.
Reciprocating pump 10 has three suction valve seats 30 and three pressure valve seats 52 altogether, and wherein, these suction valve seats 30 and these pressure valve seats 52 all limit imaginary equilateral triangle.Imaginary leg-of-mutton central point is arranged on pump longitudinal axis 64, but the imaginary triangle of the imaginary triangle relative jam valve seat 30 of pressure valve seat 52 rotates with the angle α of 25 ° around pump longitudinal axis 64.
On the axial direction about pump longitudinal axis 64, the support backplate 74 of being made up of plastic materials is connected on the pump housing 18, and this support backplate has three columniform supporting sleeves 78 that are orientated alignedly with piston longitudinal axis 76 respectively.Supporting sleeve 78 welds together with the annular wall 80 of the pump housing 18 respectively, and this annular wall is inserted in corresponding supporting sleeve 78 and surrounded seal ring 82, and sealing circle abuts on piston 22 hermetically with sealing lip.
Supporting backplate 74 is supported on guiding backplate 84 in the axial direction.Guiding backplate 84 has three columniform guide sleeves, wherein, in Fig. 1, can see guide sleeves 86.Guide sleeves 86 constructs for the induction element of piston 22 and with corresponding piston longitudinal axis 76 and is orientated coaxially.Guide sleeves 84 forms the lid of constructing protrudingly, and this lid is placed on oblique disk shell 88, and swash plate 90 is bearing in this oblique disk shell in the mode that can rotate around pump longitudinal axis 64.Each piston 20 is pressed onto on swash plate 90 by return spring 92.This can realize and make piston 20 by rotational motion to-and-fro motion on the axial direction about pump longitudinal axis 64 of swash plate 90, thereby makes the volume periodic variation of pump chamber 20.Known by common mode to the driving of swash plate 90 and therefore do not illustrate in the accompanying drawings drive motor itself, for example motor is realized, and this drive motor connects with swash plate 90 by the transmission device 94 only schematically showing in Fig. 1.
If piston 22 is motion backward in the direction that deviates from pump head 12, liquid is inhaled in pump chamber 20 via suction valve chamber 34 and suction valve passage 32 by aspirating entrance 14 so, wherein, the effect that suction valve closed shape 28 is resisted suction valve closing spring 46 is lifted away from and discharges suction valve passage 32 from suction valve seat 30.At this, liquid can flow through on suction valve closing spring 46 sides in suction chamber 34 inside and therefore in suction valve chamber 34, only suffer very little flow loss.
And if then piston 22 travels forward in the direction towards pump head 12, suction valve closed shape 28 is transitioned in its operating position so, in this operating position, suction valve closed shape abuts on suction valve seat 30, as shown at Fig. 3, Fig. 4 and Fig. 5 hermetically.Then, liquid is placed under pressure in pump chamber 20, until the closing force of pressure valve closed shape 48 renitency valve closing springs 50 is lifted away from from pressure valve seat 52, and is released in thus mobile connection the between pump chamber 20 and central compartment 56.Pressure valve closing spring 50 is supported on central inserting member 58, and the passage 60 of this central authorities' inserting member is discharged by central closed shape 62, thereby the liquid that makes to be placed under pressure can flow to pressure export 16 by pressure line 66.
Liquid can be placed under the pressure that exceedes 100 bar in pump chamber 20.Although material thickness is relatively little, the pump housing 18 of being made up of plastic materials still can bear the high pressure of liquid.To this, as explained above, pressure valve seat 52 the radial direction about pump longitudinal axis 64 and week upwards relative jam valve seat 30 stagger and arrange.Therefore, reciprocating pump 10 is characterised in that and has very high mechanical load ability and relatively little material thickness.
Claims (10)
1. the reciprocating pump for high-pressure cleaning appliance, described reciprocating pump has multiple pump chambers (20), can insert respectively in these pump chambers by reciprocating piston (22), and these pump chambers form to flow by suction valve (24) and suction entrance (14) respectively and are connected, and form to flow by pressure valve (26) and pressure export (16) and be connected, wherein, described suction valve (24) comprises suction valve closed shape (28), the closed physical efficiency of described suction valve abuts on suction valve seat (30) hermetically, and wherein, described pressure valve (26) comprises pressure valve closed shape (48), the closed physical efficiency of described pressure valve abuts on pressure valve seat (52) hermetically, wherein, described pressure valve seat (52) pump longitudinal axis relative to described suction valve seat (30) (64) has different radial spacings, it is characterized in that, described pressure valve seat (52) about described pump longitudinal axis (64) week of described reciprocating pump (10) upwards relatively described suction valve seat (30) stagger and arrange.
2. reciprocating pump according to claim 1, is characterized in that, described pressure valve seat (52) staggers and arranges with the angle of 10 ° to 40 ° about the relatively described suction valve seat of described pump longitudinal axis (64) (30).
3. reciprocating pump according to claim 1 and 2, is characterized in that, described pressure valve seat (52) is arranged on identical height with described suction valve seat (30) in the axial direction about described pump longitudinal axis (64).
4. according to the reciprocating pump described in any one in the claims, it is characterized in that, described reciprocating pump (10) has three suction valve seats (30) of arranging evenly distributedly around described pump longitudinal axis (64) and three pressure valve seats (52) of arranging evenly distributedly around described pump longitudinal axis (64).
5. according to the reciprocating pump described in any one in the claims, it is characterized in that, described reciprocating pump (20) comprises the pump housing (18) and pump head (12), wherein, described pump head (12) has described suction entrance (14) and described pressure export (16), and wherein, the described pump housing (18) comprises described pump chamber (20) and holds described suction valve and described pressure valve (24, 26), and wherein, described pump head (12) is placed on the edge triangular in shape (70) of the described pump housing (18), wherein, in the plan view of the described pump housing (18), described suction valve (24) is arranged in the corner region of described edge (70), and in the plan view of the described pump housing (18), described pressure valve (26) is surrounded by columniform inwall (72) in the inside of described edge (70).
6. according to the reciprocating pump described in any one in the claims, it is characterized in that, described suction valve (24) has respectively suction valve passage (32) and suction valve closing spring (46), described suction valve passage capable of being is sealed by described suction valve closed shape (28), described suction valve closing spring loads described suction valve closed shape (28) with spring force in the direction towards described suction valve passage (32), wherein, described suction valve closing spring (46) has the mode of axial spacing to locate with relatively described suction valve passage (32).
7. reciprocating pump according to claim 6, it is characterized in that, described suction valve closing spring (46) is arranged in suction valve chamber (34), described suction valve chamber forms to flow by described suction valve passage (32) and pump chamber (20) and is connected, wherein, keeping arm (36) has the mode of axial spacing to stretch in described suction valve chamber (34) with relatively described suction valve passage (32), and described suction valve closing spring (46) is supported on described keeping arm.
8. reciprocating pump according to claim 7, is characterized in that, described keeping arm (36) constructs the guide portion for suction valve closed shape (28).
9. according to the reciprocating pump described in claim 7 or 8, it is characterized in that, described keeping arm (36) has break-through opening (38), and described break-through opening is run through by described suction valve closed shape (28).
10. reciprocating pump according to claim 9, it is characterized in that, described suction valve closing spring (46) is tensioning between described keeping arm and described suction valve closed shape (28) in the side of described suction valve passage of deviating from of described keeping arm (36) (32).
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| PCT/EP2012/050869 WO2013107520A1 (en) | 2012-01-20 | 2012-01-20 | Piston pump for a high-pressure cleaning device |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN104053907A true CN104053907A (en) | 2014-09-17 |
| CN104053907B CN104053907B (en) | 2016-09-14 |
Family
ID=45524553
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201280067559.5A Active CN104053907B (en) | 2012-01-20 | 2012-01-20 | Piston pump for high-pressure cleaning appliance |
Country Status (5)
| Country | Link |
|---|---|
| US (1) | US20140328701A1 (en) |
| EP (1) | EP2805050B1 (en) |
| CN (1) | CN104053907B (en) |
| BR (1) | BR112014011579A2 (en) |
| WO (1) | WO2013107520A1 (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN107605688A (en) * | 2016-07-11 | 2018-01-19 | 莱乌科股份公司 | For distributing the pump of liquid |
Families Citing this family (17)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US11578710B2 (en) | 2019-05-02 | 2023-02-14 | Kerr Machine Co. | Fracturing pump with in-line fluid end |
| US11739748B2 (en) | 2019-05-14 | 2023-08-29 | Halliburton Energy Services, Inc. | Pump fluid end with easy access suction valve |
| US11261863B2 (en) | 2019-05-14 | 2022-03-01 | Halliburton Energy Services, Inc. | Flexible manifold for reciprocating pump |
| US11231111B2 (en) | 2019-05-14 | 2022-01-25 | Halliburton Energy Services, Inc. | Pump valve seat with supplemental retention |
| US11965503B2 (en) | 2019-05-14 | 2024-04-23 | Halliburton Energy Services, Inc. | Flexible manifold for reciprocating pump |
| US10808846B1 (en) | 2019-05-14 | 2020-10-20 | Halliburton Energy Services, Inc. | Pump plunger with wrench features |
| US11560888B2 (en) | 2019-05-14 | 2023-01-24 | Halliburton Energy Services, Inc. | Easy change pump plunger |
| US11105327B2 (en) | 2019-05-14 | 2021-08-31 | Halliburton Energy Services, Inc. | Valve assembly for a fluid end with limited access |
| US11441687B2 (en) | 2019-05-14 | 2022-09-13 | Halliburton Energy Services, Inc. | Pump fluid end with positional indifference for maintenance |
| US10941766B2 (en) | 2019-06-10 | 2021-03-09 | Halliburton Energy Sendees, Inc. | Multi-layer coating for plunger and/or packing sleeve |
| US11280326B2 (en) | 2019-06-10 | 2022-03-22 | Halliburton Energy Services, Inc. | Pump fluid end with suction valve closure assist |
| US10808851B1 (en) | 2019-06-10 | 2020-10-20 | Halliburton Energy Services, Inc. | Multi-material frac valve poppet |
| US10989188B2 (en) | 2019-07-26 | 2021-04-27 | Halliburton Energy Services, Inc. | Oil field pumps with reduced maintenance |
| US10677380B1 (en) | 2019-07-26 | 2020-06-09 | Halliburton Energy Services, Inc. | Fail safe suction hose for significantly moving suction port |
| DE102020131798A1 (en) | 2020-12-01 | 2022-06-02 | Alfred Kärcher SE & Co. KG | PISTON PUMP FOR A HIGH PRESSURE CLEANING DEVICE |
| DE102020131796A1 (en) | 2020-12-01 | 2022-06-02 | Alfred Kärcher SE & Co. KG | PISTON PUMP FOR A HIGH PRESSURE CLEANING DEVICE |
| JP2023151480A (en) * | 2022-03-31 | 2023-10-16 | 川崎重工業株式会社 | Rotary swash plate-type hydraulic pump |
Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US2969951A (en) * | 1957-05-31 | 1961-01-31 | Dresser Ind | Pump valve |
| US3133503A (en) * | 1962-05-25 | 1964-05-19 | Bendix Corp | Hydraulic pressure transformer |
| US3411453A (en) * | 1965-03-29 | 1968-11-19 | Bennes Marrel | Swash plate hydraulic pumps having axially disposed pistons |
| CN2544115Y (en) * | 2001-10-22 | 2003-04-09 | 台州市亿力电器有限公司 | Small sized high-pressure water pump |
| CN201295683Y (en) * | 2008-10-21 | 2009-08-26 | 罗昌国 | High pressure washer |
| CN101663487A (en) * | 2007-04-20 | 2010-03-03 | 阿尔弗雷德·凯驰两合公司 | Reciprocating pump for a high-pressure cleaning device |
Family Cites Families (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE19548498C2 (en) * | 1995-12-22 | 1998-07-23 | Kaercher Gmbh & Co Alfred | High pressure cleaning device |
| US8337166B2 (en) * | 2001-11-26 | 2012-12-25 | Shurflo, Llc | Pump and pump control circuit apparatus and method |
| DE102005050009B4 (en) * | 2005-10-11 | 2007-07-05 | Alfred Kärcher Gmbh & Co. Kg | High-pressure cleaner |
| DE102007003521B4 (en) | 2007-01-18 | 2011-06-09 | Alfred Kärcher Gmbh & Co. Kg | Piston pump for a high-pressure cleaner |
| DE102007020299A1 (en) * | 2007-04-20 | 2008-10-23 | Alfred Kärcher Gmbh & Co. Kg | Piston pump for a high-pressure cleaner |
| US20110189031A1 (en) * | 2010-02-01 | 2011-08-04 | Da Quan Zhang | Method and apparatus for improved, high-pressure, fluid pump |
-
2012
- 2012-01-20 WO PCT/EP2012/050869 patent/WO2013107520A1/en active Application Filing
- 2012-01-20 BR BR112014011579A patent/BR112014011579A2/en not_active Application Discontinuation
- 2012-01-20 CN CN201280067559.5A patent/CN104053907B/en active Active
- 2012-01-20 EP EP12700837.3A patent/EP2805050B1/en active Active
-
2014
- 2014-07-17 US US14/334,021 patent/US20140328701A1/en not_active Abandoned
Patent Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US2969951A (en) * | 1957-05-31 | 1961-01-31 | Dresser Ind | Pump valve |
| US3133503A (en) * | 1962-05-25 | 1964-05-19 | Bendix Corp | Hydraulic pressure transformer |
| US3411453A (en) * | 1965-03-29 | 1968-11-19 | Bennes Marrel | Swash plate hydraulic pumps having axially disposed pistons |
| CN2544115Y (en) * | 2001-10-22 | 2003-04-09 | 台州市亿力电器有限公司 | Small sized high-pressure water pump |
| CN101663487A (en) * | 2007-04-20 | 2010-03-03 | 阿尔弗雷德·凯驰两合公司 | Reciprocating pump for a high-pressure cleaning device |
| CN201295683Y (en) * | 2008-10-21 | 2009-08-26 | 罗昌国 | High pressure washer |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN107605688A (en) * | 2016-07-11 | 2018-01-19 | 莱乌科股份公司 | For distributing the pump of liquid |
Also Published As
| Publication number | Publication date |
|---|---|
| CN104053907B (en) | 2016-09-14 |
| BR112014011579A2 (en) | 2017-05-09 |
| EP2805050B1 (en) | 2016-07-27 |
| US20140328701A1 (en) | 2014-11-06 |
| EP2805050A1 (en) | 2014-11-26 |
| WO2013107520A1 (en) | 2013-07-25 |
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