CN106168210A - Displacement pump - Google Patents
Displacement pump Download PDFInfo
- Publication number
- CN106168210A CN106168210A CN201610336904.0A CN201610336904A CN106168210A CN 106168210 A CN106168210 A CN 106168210A CN 201610336904 A CN201610336904 A CN 201610336904A CN 106168210 A CN106168210 A CN 106168210A
- Authority
- CN
- China
- Prior art keywords
- traction
- drive shaft
- axis
- pump
- described drive
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
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Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
- F04C15/0057—Driving elements, brakes, couplings, transmission specially adapted for machines or pumps
- F04C15/0061—Means for transmitting movement from the prime mover to driven parts of the pump, e.g. clutches, couplings, transmissions
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
- F04C15/0042—Systems for the equilibration of forces acting on the machines or pump
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C2/00—Rotary-piston machines or pumps
- F04C2/08—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
- F04C2/12—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type
- F04C2/14—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C2240/00—Components
- F04C2240/50—Bearings
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C2240/00—Components
- F04C2240/60—Shafts
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Details And Applications Of Rotary Liquid Pumps (AREA)
- Rotary Pumps (AREA)
- Details Of Reciprocating Pumps (AREA)
- Reciprocating Pumps (AREA)
Abstract
A kind of displacement pump, comprising: i) drive shaft (2)；Ii) axis of traction (3), it draws described drive shaft (2) and rotates, described axis of traction (3) is coaxial with described drive shaft (2), receiving base (6) from an end including another between described axis of traction (3) and described drive shaft (2), inside described receiving base (6), described axis of traction (3) and described drive shaft (2) include shaft coupling in combination, and any radial load from described axis of traction (3) can be transferred to described drive shaft (2) by described shaft coupling；The stationary support structure (4) of the most described drive shaft (2), comprising:-support member (40), described drive shaft (2) can rotate relative to described support member (40)；-neutralizing device, its neutralization is carried on the radial load on described axis of traction (3) and substantially overlaps with one or more sliding bearings, and these one or more sliding bearings are radially clipped between described drive shaft (2) and support member (40)；The one or more sliding bearing includes at least one first sliding bearing (41)；Iv) at least one first thrust bearing (71), it axially adjoins the Part I (33) of described axis of traction (3) directly or indirectly to neutralize and being carried on the axial load on described axis of traction (3).
Description
Technical field
The present invention relates to displacement pump, particularly to gear pump.Gear pump means the volume change of the engagement induction utilizing two roll main bodies and transfers its energy in fluid.
Background technology
Known gear pump includes:
-two cog wheels, it is engaged with each other；
-drive shaft, it drives one of described expection cog wheel；
-axis of traction, it draws described drive shaft, and this axis of traction partly extends at the case inside of described pump, and extends to described hull outside, thus receives driving torque.In this technical field, axis of traction is also referred to as support member or hub.
Inside this pump case, this axis of traction is supported by roller bearing (such as two-row ball bearing), and this roller bearing is used for neutralizing axial stress and radial stress, prevents it to be transferred in drive shaft.
The shortcoming of this structure solution is the cost of this class bearing, and its size.It is true that the cost of these parts and size reflect cost and the overall dimension of this pump.
Summary of the invention
In this article, technical assignment based on the present invention is to provide and cost and overall dimension can be made to minimize, and allows to carry out the pump of operation the most reliably simultaneously.
The technical assignment stated and objectives are by including that the gear pump of technical characteristic disclosed in one or more claim substantially realizes.
Accompanying drawing explanation
Referring to the drawings, to the gear pump of the present invention preferably but rough, the indefiniteness of the most exclusive embodiment describe, contribute to being more fully understood that the other feature and advantage of the present invention, wherein:
-Fig. 1 illustrates the schematic diagram of pump that can be incorporated herein；
-Fig. 2 and 3 illustrates two orthogonal sectional views of a part for the pump of the present invention；
-Figure 4 and 5 illustrate two orthogonal sectional views of a part for the pump of the alternative embodiment according to the present invention.
Detailed description of the invention
In the accompanying drawings, reference 1 represents displacement pump, particularly gear pump.This gear and the fluid interaction transmitted by described pump, determine that energy increases.
As noted, gear pump means the volume change of the engagement induction utilizing two roll main bodies (usually cog wheel) to determine that energy is transferred to the pump of fluid.
In alternative embodiments, this pump can be, such as, having the pump of piston, this piston slides in corresponding base, and (in general wherein said piston and base thereof are rotated by swash plate traction, in the art, such pump is known, is not described in further detail).
This pump 1 includes:
-drive shaft 2；
-axis of traction 3, it draws described drive shaft 2 and rotates.
In a preferred embodiment, this pump 1 is gear pump and advantageously, this drive shaft 2 is bound at least one in described gear regularly, and this determines that (described gear and the roll main body directly contacting fluid overlap for the increase of fluid energy；Advantageously, at least one in this drive shaft 2 and described roll main body is single one-body molded main body；Advantageously, this roll main body is cog wheel).
This axis of traction 3 may be operably coupled to this drive shaft 2 and radial load be transferred to described drive shaft 2, is crimped to the device for neutralizing its axial load simultaneously.
This axis of traction 3 is directly or indirectly placed between electromotor (typically type of internal combustion engine) and the described drive shaft 2 for driving described pump 1 by transfer element.
This pump 1 includes external shell 7.This external shell 7 is a part for the protective cover of described pump.Advantageously, this external shell 7 is obtained by casting.
In the specific embodiment shown in example, this drive shaft 2 is positioned at the inside of the housing 7 of described pump 1.This axis of traction 3 is prominent to be connected directly or indirectly to electromotor in the outside of housing 7.Especially, the part at the axis of traction 3 outside housing 7 limits the PTO that may be operably coupled to described electromotor.
Described housing 7 includes that the mouth 73 for axis of traction 3 is with through described housing 7.
This pump 1 also includes the stationary support structure 4 for drive shaft 2.
This supporting construction 4 includes:
-support member 40, described drive shaft 2 can rotate relative to this support member 40；Advantageously, this support member 40 is in single main body with aforementioned housing 7.
-neutralize device, its radial load being carried on this axis of traction 3 for neutralization (and owing to described axle 3 does not include that bearing is to keep out described radial load, it is transferred to the radial load of described drive shaft 2), this neutralization device arrives in described drive shaft 2 for neutralizing and originates from the radial load (such as, owing to being transmitted) of the element resting upon trip by the motion of bevel gear pair or universal joint；This neutralization device generally comprises/overlaps one or more sliding bearing (not having rolling element), and these one or more sliding bearings are radially clipped between described drive shaft 2 and described support member 40 (it supports this drive shaft 2)；The one or more sliding bearing includes at least one first sliding bearing 41.The slidingsurface of this first sliding bearing 41 is cylindrical surface, and this cylindrical surface encapsulates the rotary shaft of this drive shaft 2.This first sliding bearing 41 for commercial type and can include steel and politef.This first sliding bearing 41 is lubrication.
This clutch shaft bearing 41 is advantageously single cylinder-shaped body.
This clutch shaft bearing 41 is static.This drive shaft 2 rotates inside this clutch shaft bearing 41.This clutch shaft bearing 41 may pass through intermediate layer lubricant with drive shaft 2() and this support member 40 contact.But, this clutch shaft bearing 41 does not contacts with this axis of traction 3.
The radial thickness of this clutch shaft bearing 41 is included between 0.5 and 3 millimeter.Advantageously, the ratio between axial length and the external diameter of this clutch shaft bearing 41 is included between 0.5 and 15.
This pump 1 also includes at least one thrust bearing 71, and this at least one thrust bearing 71 the most axially adjoins the Part I 33 of this axis of traction 3 to neutralize and being carried on the axial load on this axis of traction 3.
Such as, in the case of Fig. 2, this thrust bearing 71 abuts directly against the Part I of this axis of traction 3.In the case of Fig. 4, as the most preferably explained, this thrust bearing 71 adjoins described Part I 33 by inserting the element that reference is 31 and 711.
Especially, this pump 1 includes paired thrust bearing 71, the Part I 33 of this axis of traction 3 or constraint and be fixedly attached to the element of this Part I 33 and be axially clipped between described paired thrust bearing 71, in order to neutralizes and is carried on the axial load on this axis of traction 3.In this way, the axial load originating from axis of traction 3 will not be transferred in drive shaft 2.Paired thrust bearing 71 is paired axial plain bearing (therefore, not having rolling element).
The Part I 33 of this axis of traction 3 includes radially projecting and around the circumferentially extending part 34 of the rotary shaft of axis of traction 3.
This paired thrust bearing 71 is one-body molded with described supporting construction 4 or is bound to described supporting construction 4 regularly.This paired thrust bearing 71 is static.
In a preferred embodiment, paired thrust bearing 71 includes paired slip ring 710.This slip ring 710 is advantageously placed in parallel side by side and preferably with preset distance.Especially, described ring 710 is perpendicular to the rotary shaft extension of described axis of traction 3.Advantageously, the distance that described ring 710 is separated by is less than 10 millimeters.
Advantageously, this paired thrust bearing 71 inserts between this first sliding bearing 41 and mouth 73, and this mouth 73 is by described housing 7.Advantageously, the axial width of each thrust bearing in described thrust bearing 71 is included between 0.5 and 3 millimeter.
It is included between 20 to 50 millimeters at thrust bearing 71 with through the minimum range the mouth 73 of this housing.
This clutch shaft bearing 41 and being included between 25 to 70 millimeters through the minimum range the mouth 73 of this housing.
As illustrated in accompanying drawing, this axis of traction 3 is not by roller bearing supports.Advantageously, this drive shaft 2 is not by roller bearing supports.
This axis of traction 3 and drive shaft 2 are coaxial, both this in one include base 6, described base 6 is for accommodating another end.Advantageously, this axis of traction 3 and drive shaft 2 engage each other in the inside accommodating base 6.
In the inside accommodating base, this axis of traction 3 and drive shaft 2 include shaft coupling in combination, and this shaft coupling can make any radial load be transferred to this drive shaft 2 from this axis of traction 3.
Any radial load can be made to include this axis of traction 3 and the lateral part of drive shaft 2 from the shaft coupling that this axis of traction 3 is transferred to this drive shaft 2, and the shape of this lateral part is complementary and is fitted to each other.Therefore, the center of this axle 2 and 3 can be corrected in this lateral part.
In the inside of this receiving base 6, described axis of traction 3 and described drive shaft 2 include band tooth transmitting device in combination, for being transmitted to described drive shaft 2. from axis of traction 3 by driving torque
This toothed means acts on the Part I 9 of this axle 2 and axle 3.
For transmitting the shape complementarity partial action Part II 90 (as it was noted above, this Part II 90 also is able to make described two axles center) at this axle 2 and axle 3 of radial load.Typically, the first and second axles 9,90 of above-mentioned restriction are adjacent.
In a preferred embodiment, during this receiving base 6 is molded in described axis of traction 3.Therefore, this drive shaft 2 is prominent inside axis of traction 3.In a preferred embodiment, this drive shaft 2 has more than first tooth 21, and this more than first tooth 21 engages with more than second tooth 35 belonging to described axis of traction 3.Advantageously, this more than first tooth 21 is radially projecting from the base portion of the rotary shaft away from described axis of traction 3, and this more than second tooth 35 is radially projecting from the base portion of the rotary shaft towards described axis of traction 3 simultaneously.
This first sliding bearing 41 includes lubricating sleeve pipe 410, and this lubrication sleeve pipe 410 is bound to described supporting construction 4 and described drive shaft 2 regularly and rotates in described sleeve pipe 410.
Inside described housing 7, lubricating cavity 70 communicates with described first sliding bearing 41 and described paired thrust bearing 71.This pump 1 farther includes for the pipeline to lubricating cavity 70 feeding lubricant.
This can lubricate thrust bearing 71 facing with each other in lubricating cavity 70.
Advantageously, this pump 1 includes oil seal 72, and this oil seal 72 contributes to defining described lubricating cavity 71.This oil seal 72 radially extends between a part for axis of traction 3 and described housing 7.
In the embodiment shown in figs. 2 and 3, this axis of traction 3 includes shoulder 30, and this shoulder 30 inserts between described paired thrust bearing 71 and is arranged between described paired thrust bearing 71.This shoulder 30 is made with single one-body molded main body with other parts of this axis of traction 3.
In the embodiment of Figure 4 and 5, this axis of traction 3 includes circumference base 31, in the plane of the rotary shaft that this circumference base 31 is positioned at crosscutting (preferably, being perpendicular to) described axis of traction 3；Western lattice ring 32 part integrated with this traction 3 is positioned in described base 31 and extends radially out from this base 31, touching at least one thrust bearing 71 via at least one first ring 711, this first ring 711 inserts between described western lattice ring 32 and described thrust bearing 71.
The invention still further relates to the operation method of displacement pump, particularly gear with the fluid interaction transmitted by this pump to determine the increase of its energy.Described pump 1 has one or more features mentioned above.This pump 1 includes that drive shaft 2 and axis of traction 3, described axis of traction 3 draw described drive shaft 2 and rotate.Advantageously, this drive shaft 2 can be bound at least one in described gear regularly.The method comprises the steps:
-by least one thrust bearing 71 and axial load present on axis of traction 3, this thrust bearing 71 the most axially adjoins the Part I 33 of this axis of traction 3 by least one intermediary element；
-radial load being carried on described axis of traction 3 is transferred to described drive shaft 2；
-radial load of this drive shaft 2 is neutralized by one or more sliding bearings, these one or more sliding bearings encapsulate and support described drive shaft 2.
Therefore, the present invention conceived is obtained in that multiple advantage.
Especially, the overall dimension of the described pump in the present invention declines.
Use sliding bearing rather than roller bearing more compact (particularly at the axial direction of axis of traction 3) and cost-effective.Particularly, this drive shaft 2 is supported by bush(ing) bearing, and this bush(ing) bearing is applied not only to neutralize the radial load produced by axle 2, is additionally operable to neutralize the radial load originating from described axle 3.The axial load being carried on described axle 3 is neutralized by paired thrust bearing, and is therefore transferred to described axle 2.
Therefore, without departing from the inventive concept of the premise, it is also possible to make some deformation and improvement, these broadly fall into protection scope of the present invention.Additionally, all details of the present invention all may be by the element substitution of technical equivalences.In practice, all material and the size of use can be as needed for any type.
Claims (10)
1. a displacement pump, comprising:
I) drive shaft (2)；
Ii) axis of traction (3), it draws described drive shaft (2) and rotates, described axis of traction (3) is coaxial with described drive shaft (2), receiving base (6) from an end including another between described axis of traction (3) and described drive shaft (2), inside described receiving base (6), described axis of traction (3) and described drive shaft (2) include shaft coupling in combination, and any radial load from described axis of traction (3) can be transferred to described drive shaft (2) by described shaft coupling；
The stationary support structure (4) of the most described drive shaft (2), comprising:
-support member (40), described drive shaft (2) can rotate relative to described support member (40)；
-neutralizing device, its neutralization is carried on the radial load on described axis of traction (3) and substantially overlaps with one or more sliding bearings, and these one or more sliding bearings are radially clipped between described drive shaft (2) and support member (40)；The one or more sliding bearing includes at least one first sliding bearing (41)；
Iv) at least one first thrust bearing (71), it axially adjoins the Part I (33) of described axis of traction (3) directly or indirectly to neutralize and being carried on the axial load on described axis of traction (3).
Pump the most according to claim 1, it is characterised in that described pump is gear pump, and include at least one pair of cog wheel, at least one pair of cog wheel described and fluid interaction, so that it is determined that the increase of fluid energy；Described drive shaft (2) is bound at least one in described cog wheel regularly.
Pump the most according to claim 1, it is characterized in that, the described shaft coupling that any radial load from described axis of traction (3) can be transferred to described drive shaft (2) includes described axis of traction (3) and the lateral part of described drive shaft (2), and described lateral part shape is complementary and is fitted to each other；
In addition to any radial load from described axis of traction (3) can be transferred to the described shaft coupling of described drive shaft (2), internal described receiving base (6), described axis of traction (3) and described drive shaft (2) include band toothed wheel transmission equipment in combination, and driving torque is transmitted to described drive shaft (2) by described band toothed wheel transmission equipment from described axis of traction (3).
Pump the most according to claim 1, it is characterized in that, described first sliding bearing (41) includes lubricating sleeve pipe (410), and described lubrication sleeve pipe (410) is bound to described supporting construction (4) and described drive shaft (2) regularly and rotates in described lubrication sleeve pipe (410).
Pump the most according to claim 1, it is characterised in that it includes external shell (7), described axis of traction (3) is prominent in the outside of described housing (7), so as to be connected directly or indirectly to electromotor.
Pump the most according to claim 1, it is characterised in that there is lubricating cavity (70) in the inside of described housing (7), described lubricating cavity (70) and described first sliding bearing (41) and connect with described thrust bearing (71).
Pump the most according to claim 1, it is characterized in that, described at least one thrust bearing (71) includes paired thrust bearing, the Part I (33) of described axis of traction (3) includes shoulder (30), and described shoulder (30) adjoins described paired thrust bearing (71) and is arranged between described paired thrust bearing (71).
Pump the most according to claim 1, it is characterized in that, described axis of traction (3) includes circumference base (31), in the plane of the rotary shaft that described circumference base (31) is positioned at tangent described axis of traction (3), and this pump (1) includes western lattice ring (32), described western lattice ring (32):
-be at least partially disposed in described circumference base (31)；
-contacting described thrust bearing (71) by least one first ring (711), this first ring (711) inserts between described western lattice ring (32) and described thrust bearing (71).
9. according to above pump described in any one claim, it is characterised in that described axis of traction (3) and described drive shaft (2) be not by roller bearing supports.
10. the operation method of a gear pump, described gear and the fluid interaction transmitted by this pump, so that it is determined that the increase of its energy, described pump includes drive shaft (2) and axis of traction (3), described drive shaft (2) can be bound at least one in described gear regularly, described axis of traction (3) draws described drive shaft (2) and rotates, and described method comprises the steps:
-neutralizing axial load present on axis of traction (3) by least one thrust bearing (71), this thrust bearing (71) the most axially adjoins the Part I (33) of described axis of traction (3) by least one intermediary element；
-only the radial load being carried on described axis of traction (3) is transferred to described drive shaft (2)；
-it being carried on the radial load in described drive shaft (2) by the neutralization of one or more sliding bearings, the one or more sliding bearing encapsulates described drive shaft (2).
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| ITUB20150780 | 2015-05-20 | ||
| IT102015000016170 | 2015-05-20 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN106168210A true CN106168210A (en) | 2016-11-30 |
| CN106168210B CN106168210B (en) | 2020-07-14 |
Family
ID=53900996
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201610336904.0A Active CN106168210B (en) | 2015-05-20 | 2016-05-20 | Displacement pump |
Country Status (2)
| Country | Link |
|---|---|
| EP (1) | EP3096016B1 (en) |
| CN (1) | CN106168210B (en) |
Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US2801593A (en) * | 1954-05-03 | 1957-08-06 | Roper Corp Geo D | Rotary pump |
| US6244842B1 (en) * | 1999-11-09 | 2001-06-12 | James B. Tieben | Pump |
| CN2575331Y (en) * | 2002-10-17 | 2003-09-24 | 关岐生 | Spiale horizontal unit construction water pump capable of using B3 type motor |
| WO2012103926A1 (en) * | 2011-01-31 | 2012-08-09 | Robert Bosch Gmbh | Gear pump |
Family Cites Families (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US2412588A (en) * | 1943-05-31 | 1946-12-17 | Pesco Products Co | Gear divider with pressure loaded bushings |
-
2016
- 2016-05-16 EP EP16169752.9A patent/EP3096016B1/en active Active
- 2016-05-20 CN CN201610336904.0A patent/CN106168210B/en active Active
Patent Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US2801593A (en) * | 1954-05-03 | 1957-08-06 | Roper Corp Geo D | Rotary pump |
| US6244842B1 (en) * | 1999-11-09 | 2001-06-12 | James B. Tieben | Pump |
| CN2575331Y (en) * | 2002-10-17 | 2003-09-24 | 关岐生 | Spiale horizontal unit construction water pump capable of using B3 type motor |
| WO2012103926A1 (en) * | 2011-01-31 | 2012-08-09 | Robert Bosch Gmbh | Gear pump |
Also Published As
| Publication number | Publication date |
|---|---|
| EP3096016A1 (en) | 2016-11-23 |
| EP3096016B1 (en) | 2021-04-07 |
| CN106168210B (en) | 2020-07-14 |
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