CN108591052A - Impeller of pump - Google Patents
Impeller of pump Download PDFInfo
- Publication number
- CN108591052A CN108591052A CN201810184056.5A CN201810184056A CN108591052A CN 108591052 A CN108591052 A CN 108591052A CN 201810184056 A CN201810184056 A CN 201810184056A CN 108591052 A CN108591052 A CN 108591052A
- Authority
- CN
- China
- Prior art keywords
- bushing
- blade part
- impeller
- pump
- peripheral surface
- 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
Links
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
- F04C15/0003—Sealing arrangements in rotary-piston machines or pumps
- F04C15/0007—Radial sealings for working fluid
- F04C15/0015—Radial sealings for working fluid of resilient material
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01P—COOLING OF MACHINES OR ENGINES IN GENERAL; COOLING OF INTERNAL-COMBUSTION ENGINES
- F01P5/00—Pumping cooling-air or liquid coolants
- F01P5/10—Pumping liquid coolant; Arrangements of coolant pumps
-
- 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
- F04C5/00—Rotary-piston machines or pumps with the working-chamber walls at least partly resiliently deformable
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01P—COOLING OF MACHINES OR ENGINES IN GENERAL; COOLING OF INTERNAL-COMBUSTION ENGINES
- F01P3/00—Liquid cooling
- F01P3/20—Cooling circuits not specific to a single part of engine or machine
- F01P3/202—Cooling circuits not specific to a single part of engine or machine for outboard marine engines
-
- 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
- F04C2210/00—Fluid
- F04C2210/10—Fluid working
- F04C2210/1094—Water
-
- 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
- F04C2240/20—Rotors
-
- 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
- F04C2250/00—Geometry
- F04C2250/20—Geometry of the rotor
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
- F05C—INDEXING SCHEME RELATING TO MATERIALS, MATERIAL PROPERTIES OR MATERIAL CHARACTERISTICS FOR MACHINES, ENGINES OR PUMPS OTHER THAN NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES
- F05C2251/00—Material properties
- F05C2251/10—Hardness
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Structures Of Non-Positive Displacement Pumps (AREA)
- Details And Applications Of Rotary Liquid Pumps (AREA)
Abstract
Problem of the present invention is that, the diameter of impeller will not be made to become larger, the manufacturing cost of impeller will not be made to increase, by increase be installed on shell when interference volume by make blade part generate reaction force become larger, to prevent blade part from being detached with the inner peripheral surface of shell, enhance discharging performance, which can be addressed by following impeller of pump, and impeller of pump (1) has：Cylindric bushing (13), the eccentric position that can be rotationally retained at via rotary shaft (3) inside the pump case of cylindrical shape；And multiple blade parts (11), it is fixed on the peripheral surface of the bushing (13), with radiated entend, the inside of the pump case is divided into multiple subregions (14), the multiple blade part (11) is made of rubbery elastic materials respectively, and is formed as rolling tiltedly towards the direction of rotation of the bushing (13) relative to the radiation direction of the rotary shaft (3) from the bushing (13).
Description
Technical field
The present invention relates to the impeller of pump of cooling water pump, burr pump for outboard motor etc., more particularly to can
Prevent blade part from the impeller of pump of discharging performance is detached, enhanced with the inner peripheral surface of pump case.
Background technology
Currently, the impeller of pump as cooling water pump, the burr pump that can be used for outboard motor etc., it is known to shown in Fig. 4
The impeller of pump (patent document 1,2) of construction.
In Fig. 4,100 be the impeller of pump for the inside that can be rotationally retained at pump case 200.Impeller of pump 100 is mounted on
It is configured at the rotary shaft 300 of the eccentric position in pump case 200.Impeller of pump 100 have be made of rubbery elastic materials it is more
A blade part 110,210 Elastic Contact of inner peripheral surface with pump case 200.
The inside of pump case 200 is separated into multiple subregions 120 by this impeller of pump 100 by multiple blade parts 110.Work as pump
When being rotated via rotary shaft 300 with impeller 100, phase of each blade part 110 towards the direction of rotation (arrow R) of impeller of pump 100
Negative direction is bent.When impeller of pump 100 rotates, the subregion 120 between adjacent two blade parts 110,110 is in rotary shaft
300 close to the inner peripheral surface 210 of pump case 200 side smaller volume, inner peripheral surface 210 of the rotary shaft 300 apart from pump case 200 farther out
Side volume enlargement.
When the volume enlargement of subregion 120 (direction of arrow R1), in the subregion 120 via being set to pump case 200 not
The suction inlet of diagram sucks water from outside.Also, when the volume of subregion 120 is gradually reduced (direction of arrow R2), from this point
Water is discharged to outside via the outlet (not shown) for being set to pump case 200 for area 120.
In impeller of pump 100 recorded in patent document 1, each blade part 110 is formed as relative to radiation direction direction
The opposite direction of the direction of rotation of impeller 100 tilts.
Pass through this inclination, it is possible to reduce each blade part 110 deviates nature shape when being bent due to the rotation of impeller of pump 100
The addendum modification (interference volume) of state reduces fatigue of materials caused by displacement.
Existing technical literature
Patent document
Patent document 1：Japanese Unexamined Patent Publication 63-010281 bulletins
Patent document 2：Japanese Unexamined Patent Publication 2015-074994 bulletins
But in recent years, it is desirable to enhance discharging performance in above-mentioned this impeller of pump.In order to enhance discharging performance, need
So that the reaction force that blade part 110 generates is become larger, increase the pressing force to the inner peripheral surface 210 of pump case 200, when will not be because of rotation
The hydraulic pressure of generation makes blade part 110 be detached with inner peripheral surface 210.
As the existing method that the reaction force for generating blade part 110 in impeller of pump 100 becomes larger, raising leaf is listed
The rubber hardness in piece portion 110 thickens the thickness of blade part 110 or by the length of blade part 110.
For the rubber hardness of blade part 110, in order to ensure good tensile properties and fatigue properties, Xiao A hardness
Hs (JIS K6253) is up to 70, is not preferably arranged to the value or more.Therefore, the reaction force in order to make blade part 110 generate
Become larger, the rubber hardness of blade part 110 can not be improved.
If the thickness of blade part 110 thickend, the subregion 120 between two blade parts 110,110 can narrow, therefore
Soakage and discharge rate can be reduced.It therefore, can not be by blade part 110 in order to which the reaction force for making blade part 110 generate becomes larger
Thickness thicken.
If by the length of blade part 110, the diameter of impeller of pump 100 can become larger, and can cause through a rubber
The number that sealing rubber die can manufacture tails off, thus becomes the main reason for manufacturing cost rises.Therefore, in order to make blade part 110 produce
Raw reaction force becomes larger, can not be by the length of blade part 110.
Invention content
Therefore, the present invention makes in view of the foregoing, and project is to provide impeller of pump, not will increase the straight of impeller
Diameter will not be such that the manufacturing cost of impeller rises, by increase be installed on shell when effective interference volume by make blade part generate
Reaction force becomes larger, and to prevent blade part from being detached with the inner peripheral surface of shell, can enhance discharging performance.
Other projects of the present invention become apparent according to contents below.
The above subject is solved by following invention.
At least one of in order to solve the above problems, reflect that the impeller of pump of one aspect of the present invention has：
Cylindric bushing, the eccentric position inside the pump case of cylindrical shape can be rotationally retained at via rotary shaft；
And multiple blade parts, it is fixed on the peripheral surface of the bushing, with radiated entend, the inside of the pump case is divided into multiple
Subregion,
The multiple blade part is made of rubbery elastic materials respectively, and is formed as relative to the rotation from the bushing
The radiation direction of shaft rolls oblique towards the direction of rotation of the bushing.
In accordance with the invention it is possible to provide impeller of pump below, the diameter of impeller not will increase, will not make the manufacture of impeller
Cost increase, the reaction force that effective interference volume when being installed on shell by increasing by makes blade part generate becomes larger, to anti-
Only blade part is detached with the inner peripheral surface of shell, can enhance discharging performance.
Description of the drawings
Fig. 1 is the schematic cross-sectional view for the embodiment for indicating the impeller of pump in the present invention.
Fig. 2 is the brief diagram of the incline structure of the blade part of the impeller of pump described in definition graph 1.
Fig. 3 is the enlarged drawing of the major part of impeller of pump shown in Fig. 2.
Fig. 4 is the vertical view for indicating existing impeller of pump.
Symbol description
1 impeller of pump
11 blade parts
The front end sides 11a
11b base end sides
11c middle parts
12 front ends
13 bushings
14 subregions
2 pump cases
21 inner peripheral surfaces
3 rotary shafts
Specific implementation mode
In the following, with reference to attached drawing, embodiments of the present invention will be described.
The impeller of pump of the present invention is used for cooling water pump, the burr pump etc. of outboard motor.
Fig. 1 be indicate the present invention impeller of pump embodiment schematic cross-sectional view, Fig. 2 be illustrate it is shown in FIG. 1
The brief diagram of the incline structure of the blade part of impeller of pump, Fig. 3 are the enlarged view of the main part of impeller of pump shown in Fig. 2.
In Fig. 1,1 is impeller of pump, which is maintained at the inside of pump case 2 in a manner of it can rotate.
Pump case 2 is made of metal material etc., is formed as the closed cylindrical shape of upper and lower side, for example, side has not below
The suction inlet of diagram has outlet (not shown) in upper face side.For the material of pump case 2, connect with the stronger water of corrosivity
In the case of touching, the material of excellent corrosion resistance is preferably selected.
As shown in FIG. 1 to 3, impeller of pump 1 has cylindric bushing 13 and with the radial bushing 13 that is formed in
Multiple blade parts 11 of peripheral surface.In this embodiment, impeller of pump 1 has six blade parts 11.
As shown in FIG. 2 and 3, each blade part 11 before being installed on shell under natural conditions, towards impeller of pump 1
Direction of rotation (direction shown in arrow R) tilts.It is not particularly limited the inclined method that carries out, but utilizes molding in present embodiment
Method is into line tilt.Illustrate the details of incline structure below.
In mode shown in Fig. 1, impeller 1 rotate, each blade part 11 by with pump case 2 inner peripheral surface 21 sliding contact by
Towards the opposite direction bending of the direction of rotation R of impeller 1.The rotating speed rotation that impeller 1 for example turns left right with per minute 6000.
Bushing 13 is formed by resin materials such as thermoplastic resin or thermosetting resins.It is not particularly limited the material of bushing 13,
But such as polyamide that use intensity can be selected excellent.
Each blade part 11 is formed by the rubbery elastic materials such as neoprene (CR) or nitrile rubber (NBR), with bushing 13
Peripheral surface bonding.It is not particularly limited adhesive bonding method, but can be on the basis of application of adhesive on bushing 13 by blade part
11 sintering are molded on bushing 13, or are bonded by adhesive and bushing 13 behind formed blades portion 11.
The rubber hardness of each blade part 11 can be used in order to ensure good tensile properties and fatigue properties
Rubber of the Xiao A hardness Hs (JIS K6253) in 45~75 ranges.As it is explained in detail hereinafter, due to making blade part 11 to rotation side
To inclination, therefore rubber hardness can select that fatigue properties are good, rubber of soft.But rubber hardness is less than 45 rubber
Glue is not used since rubber reaction force is too low.
Bushing 13 is mounted on and is configured in the rotary shaft 3 of the eccentric position in pump case 2, can be rotatably by the rotary shaft 3
It keeps.
Bushing 13 has axis hole 13a along central shaft, and being inserted in axis hole 13a has rotary shaft 3.In axis hole 13a
Circumferential surface is provided with keyway 13b.The parallel key 3a that the peripheral surface of rotary shaft 3 is formed is entrenched in keyway 13b, so that rotation
Axis 3 will not dally.
Bushing 13 drives rotation via rotary shaft 3 by power source (not shown) is with each blade part 11.
The front end 12 of multiple blade parts 11 and 21 Elastic Contact of inner peripheral surface of pump case 2.
In addition, the sliding contact parts being made of resin material can also be arranged in front end 12 in blade part 11, make the cunning
21 Elastic Contact of inner peripheral surface of dynamic contact component and pump case 2.Blade part 11 is covered alternatively, it is also possible to be formed as sliding contact parts
Front end 12.Sliding contact parts are preferably by formation such as the excellent fluorine resin such as resistance to sliding, polyamides.In the feelings
Under condition, can long-term, steady decrease resistance to sliding, abrasion, the damage of impeller of pump 1 can be prevented, and rotation can be reduced
Torque reduces power loss, improves fuel consumption.
As shown in Figure 1, the inside of pump case 2 is divided into multiple subregions 14 by impeller of pump 1 by multiple blade parts 11.Work as pump
When being rotated via rotary shaft 3 and bushing 13 with impeller 1, direction of rotation (in Fig. 1 arrow R institute of each blade part 11 towards impeller 1
Show direction) opposite direction bending.
At this point, the inner peripheral surface 21 that each blade part 11 presses pump case 2 by the front end side 11a comprising front end 12 generates anti-work
Firmly (restoring force).By the reaction force (restoring force), the front end side 11a of blade part 11 is crimped on the inner peripheral surface of pump case 2
21。
In the impeller of pump 1, blade part 11 is larger to the pressing force of the inner peripheral surface 21 of pump case 2, therefore can prevent spin-ended
The hydraulic pressure generated when turning detaches blade part 11 with inner peripheral surface 21.
Each subregion 14 between two blade parts 11,11 is when impeller of pump 1 rotates, in rotary shaft 3 in pump case 2
The side (left side in Fig. 1) of circumferential surface 21, the smaller volume of subregion 14, the pressure in subregion 14 is got higher, in rotary shaft 3 apart from pump
The side (right side in Fig. 2) of the inner peripheral surface 21 of shell 2 farther out, the volume enlargement of subregion 14, the pressure in subregion 14 are lower.
In the section that the volume of subregion 14 is gradually expanded (section shown in arrow R1), in the subregion 14 through not shown
Suction inlet sucks water from outside.Also, in the diminishing section of the volume of subregion 14 (section shown in arrow R2), from this point
Water is discharged to outside through not shown outlet for area 14.
Next, illustrating the incline structure of blade part based on Fig. 2 and Fig. 3.
As shown in these figures, each blade part 11 of impeller of pump 1 is formed as following shapes：Relative to self-sustaining bushing 13
The radiation direction of the central shaft 3c of rotary shaft 3, towards the direction of rotation R tilt angle thetas of bushing 13.
Since each blade part 11 is formed towards the direction of rotation R cant angle degree θ of bushing 13, as shown in Figure 1,
When the impeller of pump 1 rotates, using middle part 11c as starting point, front end side (lip) 11a is bent towards direction is reversely rotated, right
The pressing force F of the inner peripheral surface 21 of pump case 2 becomes larger, i.e., interference volume becomes larger.
Pressing force F is played a role in a manner of so that the front end side 11a of blade part 11 is restored.
Also, become larger to the pressing force F of the inner peripheral surface of pump case 21, the pressing force F (reactions that front end side 11a to be made restores
Power) act on middle part 11c.
As a result, preventing base end side 11b towards direction bending is reversely rotated, plays and retain towards direction of rotation R inclinations
The effect of state.
That is, since pressing force F becomes larger, as a result, the base end side 11b of blade part 11 can be kept towards direction of rotation R
Inclined state.
The impeller 1 is in pump case 2 when rotation, and since the interference volume of blade part 11 becomes larger, blade part 11 generates anti-
Active force becomes larger.
Being become larger by the pressing force of the inner peripheral surface 21 to pump case 2, it is therefore prevented that blade part 11 is detached with inner peripheral surface 21, therefore,
In each subregion 14 for the pump case 2 that blade part 11 separates, water will not be leaked out to other subregions.In turn, due to water in each subregion 14
It will not be leaked out to other subregions, as a result, discharging performance can be enhanced.
In addition, in the impeller 1, by making each blade part 11 be tilted towards direction of rotation R, even if the thickness of blade part 11
It is arranged than previous slightly thin situation, can also increases the pressing force F to inner peripheral surface 21.As a result, two blades can also be made
Subregion 14 between portion 11,11 becomes larger, and can increase soakage and discharge rate.
In turn, the impeller of pump 1 is by making each blade part 11 according to the distinctive incline structure of the present invention into line tilt, with
Toward comparing, diameter will not become larger.As a result, the number that can be manufactured using a rubber mold will not be reduced, will not make to be manufactured into
This rising.
Fig. 3 is the enlarged drawing of the major part of impeller of pump shown in Fig. 2.
As shown in figure 3, the length L2 of blade part 11 is only by tilt angle theta, it is required when not tilted with the blade part 11
It is elongated compared with length L1 (always with 21 sliding contact of inner peripheral surface of pump case 2 and the length of bending).
If the tilt angle theta of blade part 11 is smaller, the length L2 of blade part 11 is close to length L1, tilt angle theta
Bigger, the length L2 of blade part 11 is more more than length L1.
If the tilt angle theta of blade part 11 is too small, when the impeller 1 in shell 2 rotates, interference volume will not fully become
Greatly, required reaction force can not be generated.On the contrary, if the tilt angle theta of blade part 11 is excessive, it may when impeller 1 rotates
It will not be bent.
The preferred angle θ of blade part 11 is about 0.1 degree~10 degree or so as a result,.For the tilt angle theta, only
If when rotation angles of the base end side 11b towards direction of rotation R heeling conditions can be kept according to the above-mentioned relationship with pressing force F
.
Furthermore it is possible to suitably set the thickness T of blade part 11 according to the relationship of the internal diameter with pump case 2.In addition, blade part 11
Tilt angle theta and thickness T be preferably designed for rotation when base end side 11b can be kept towards the inclined states of direction of rotation R.
By meeting these conditions, each blade part 11 can be bent well when impeller of pump 1 rotates, and interference volume is abundant
Become larger, and generate required reaction force, as a result, discharging performance can be enhanced.
Additionally, this invention is not limited to the above embodiments, it is of course possible to be used in the limit for not departing from present subject matter
Various structures.
Claims (4)
1. a kind of impeller of pump, has：Cylindric bushing, the pump case of cylindrical shape can be rotationally retained at via rotary shaft
Internal eccentric position；And multiple blade parts, it is fixed on the peripheral surface of the bushing, with radiated entend, by the pump case
Inside be separated into multiple subregions, which is characterized in that
The multiple blade part is made of rubbery elastic materials respectively, and is formed as relative to the rotary shaft from the bushing
Radiation direction rolled towards the direction of rotation of the bushing it is oblique.
2. impeller of pump according to claim 1, which is characterized in that
The multiple blade part respectively from the base end side positioned at the side for the peripheral surface for being fixed on the bushing extend to it is described
The front end side of the inner peripheral surface sliding contact of pump case,
Also, the base end side of the blade part is formed as the radiation direction relative to the rotary shaft from the bushing towards institute
The direction of rotation for stating bushing rolls tiltedly.
3. impeller of pump according to claim 2, which is characterized in that
Be formed as the radiation relative to the rotary shaft from the bushing from the base end side of the blade part to the front end side
Direction rolls oblique towards the direction of rotation of the bushing.
4. impeller of pump according to claim 1, which is characterized in that
The multiple blade part be respectively provided with positioned at be fixed on the bushing peripheral surface side base end side and with it is described
The front end side of the inner peripheral surface sliding contact of pump case,
The multiple blade part is formed as：Even if the front end side of the blade part is pressed and be bent towards direction is reversely rotated,
The base end side still retains towards the inclined state in direction of rotation.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2017-042478 | 2017-03-07 | ||
| JP2017042478A JP6890439B2 (en) | 2017-03-07 | 2017-03-07 | Pump impeller |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN108591052A true CN108591052A (en) | 2018-09-28 |
| CN108591052B CN108591052B (en) | 2020-10-30 |
Family
ID=63444387
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201810184056.5A Active CN108591052B (en) | 2017-03-07 | 2018-03-06 | Pump impeller |
Country Status (3)
| Country | Link |
|---|---|
| US (1) | US20180258932A1 (en) |
| JP (1) | JP6890439B2 (en) |
| CN (1) | CN108591052B (en) |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN112922715B (en) * | 2021-03-01 | 2022-08-23 | 浙江沧龙动力机械有限公司 | Outboard engine cooling pump structure |
Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US20110311387A1 (en) * | 2010-06-22 | 2011-12-22 | Gm Global Technoloby Operations, Inc. | High efficiency fixed displacement vane pump |
| CN102444577A (en) * | 2010-09-30 | 2012-05-09 | 富士重工业株式会社 | Internal-gear type fluid device |
| CN204175595U (en) * | 2014-09-01 | 2015-02-25 | 浙江维新汽车配件有限公司 | A kind of engine of boat and ship rubber impeller formula water pump |
| JP2015074994A (en) * | 2013-10-07 | 2015-04-20 | Nok株式会社 | Impeller |
| CN205078443U (en) * | 2015-09-29 | 2016-03-09 | 郑泰工程机械有限公司 | Small -size mechanical water pump |
Family Cites Families (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US2899902A (en) * | 1959-08-18 | Rotary pump impeller | ||
| US2466440A (en) * | 1948-07-29 | 1949-04-05 | Kiekhaefer Elmer Carl | Impeller for rotary pumps |
| US2933046A (en) * | 1956-12-26 | 1960-04-19 | Jabsco Pump Co | Pump with flexible impeller and flexible annular cam |
| US3001480A (en) * | 1959-06-12 | 1961-09-26 | West Bend Aluminum Co | Rotary pump |
| US3053190A (en) * | 1961-04-10 | 1962-09-11 | Minnesota Rubber Co | Rotary vane type positive displacement pump |
| US3054355A (en) * | 1961-04-25 | 1962-09-18 | Lord Mfg Co | Pump |
| US4392779A (en) * | 1980-05-05 | 1983-07-12 | Brunswick Corporation | Marine drive water pump |
-
2017
- 2017-03-07 JP JP2017042478A patent/JP6890439B2/en active Active
-
2018
- 2018-03-06 CN CN201810184056.5A patent/CN108591052B/en active Active
- 2018-03-06 US US15/912,972 patent/US20180258932A1/en not_active Abandoned
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US20110311387A1 (en) * | 2010-06-22 | 2011-12-22 | Gm Global Technoloby Operations, Inc. | High efficiency fixed displacement vane pump |
| CN102444577A (en) * | 2010-09-30 | 2012-05-09 | 富士重工业株式会社 | Internal-gear type fluid device |
| JP2015074994A (en) * | 2013-10-07 | 2015-04-20 | Nok株式会社 | Impeller |
| CN204175595U (en) * | 2014-09-01 | 2015-02-25 | 浙江维新汽车配件有限公司 | A kind of engine of boat and ship rubber impeller formula water pump |
| CN205078443U (en) * | 2015-09-29 | 2016-03-09 | 郑泰工程机械有限公司 | Small -size mechanical water pump |
Also Published As
| Publication number | Publication date |
|---|---|
| JP6890439B2 (en) | 2021-06-18 |
| JP2018145901A (en) | 2018-09-20 |
| US20180258932A1 (en) | 2018-09-13 |
| CN108591052B (en) | 2020-10-30 |
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