CN1534195A - Gear pump - Google Patents
Gear pump Download PDFInfo
- Publication number
- CN1534195A CN1534195A CNA2004100352327A CN200410035232A CN1534195A CN 1534195 A CN1534195 A CN 1534195A CN A2004100352327 A CNA2004100352327 A CN A2004100352327A CN 200410035232 A CN200410035232 A CN 200410035232A CN 1534195 A CN1534195 A CN 1534195A
- Authority
- CN
- China
- Prior art keywords
- pressure
- pump
- gear
- fluid
- inner space
- 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
- 238000004891 communication Methods 0.000 claims abstract description 34
- 239000012530 fluid Substances 0.000 claims description 49
- 239000000446 fuel Substances 0.000 claims description 24
- 239000007788 liquid Substances 0.000 claims description 9
- 238000007599 discharging Methods 0.000 claims description 6
- 230000000630 rising effect Effects 0.000 claims description 3
- 238000003860 storage Methods 0.000 claims description 2
- LCGLNKUTAGEVQW-UHFFFAOYSA-N Dimethyl ether Chemical compound COC LCGLNKUTAGEVQW-UHFFFAOYSA-N 0.000 description 96
- 239000002828 fuel tank Substances 0.000 description 18
- 239000011159 matrix material Substances 0.000 description 16
- 239000011148 porous material Substances 0.000 description 16
- 238000011144 upstream manufacturing Methods 0.000 description 12
- 238000007789 sealing Methods 0.000 description 6
- 238000001704 evaporation Methods 0.000 description 5
- 230000008020 evaporation Effects 0.000 description 5
- 238000000034 method Methods 0.000 description 5
- 230000008676 import Effects 0.000 description 4
- 230000002093 peripheral effect Effects 0.000 description 4
- 230000001105 regulatory effect Effects 0.000 description 4
- 238000004804 winding Methods 0.000 description 4
- 238000002485 combustion reaction Methods 0.000 description 3
- XEEYBQQBJWHFJM-UHFFFAOYSA-N Iron Chemical group [Fe] XEEYBQQBJWHFJM-UHFFFAOYSA-N 0.000 description 2
- 238000012937 correction Methods 0.000 description 2
- 238000001514 detection method Methods 0.000 description 2
- 230000000694 effects Effects 0.000 description 2
- 230000003321 amplification Effects 0.000 description 1
- 230000015572 biosynthetic process Effects 0.000 description 1
- 238000001816 cooling Methods 0.000 description 1
- 230000005674 electromagnetic induction Effects 0.000 description 1
- 230000003116 impacting effect Effects 0.000 description 1
- 230000014759 maintenance of location Effects 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 238000003199 nucleic acid amplification method Methods 0.000 description 1
- 238000012545 processing Methods 0.000 description 1
Images
Classifications
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- 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
- F04C2/18—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 with similar tooth forms
-
- 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
- F04C11/00—Combinations of two or more machines or pumps, each being of rotary-piston or oscillating-piston type; Pumping installations
- F04C11/001—Combinations of two or more machines or pumps, each being of rotary-piston or oscillating-piston type; Pumping installations of similar working principle
-
- 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
- F04C15/0034—Sealing arrangements in rotary-piston machines or pumps for other than the working fluid, i.e. the sealing arrangements are not between working chambers of the machine
- F04C15/0038—Shaft sealings specially adapted for rotary-piston machines or 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
- 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
- F04C2/082—Details specially related to intermeshing engagement type machines or pumps
- F04C2/086—Carter
-
- 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
- F04C2210/20—Fluid liquid, i.e. incompressible
-
- 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
- F04C2210/20—Fluid liquid, i.e. incompressible
- F04C2210/201—DME
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Rotary Pumps (AREA)
- Details And Applications Of Rotary Liquid Pumps (AREA)
Abstract
A two-stage gear pump has a pump section. The pump section has an internal space that is located adjacent to a driven gear and about a cylindrical surface of the driven shaft. A discharge section of a first gear train is connected to a suction section of a second gear train with a communication passage. The internal space is connected to the communication passage with a pressure introduction passage. The pressure of the communication passage is introduced to the internal space by the pressure introduction passage, so that the pressure atmosphere of the internal space is an intermediate pressure atmosphere of the suction pressure and the discharge pressure of the pump section.
Description
[technical field]
The present invention relates to a kind of gear pump that is used for conveyance fluid under pressure.
[background technique]
Traditionally, for example in Japanese publication specification 2001-140770 number disclosed gear pump be known.This gear pump has pump portion 101 as shown in Figure 9.Pump portion 101 has two-stage gear train 111, and each grade gear train 111 has two couples of the actuation gear 111a and the driven gear 111b of engagement each other.In pump portion 101, a plurality of pump chamber 111c that are used to transmit fluid are determined by gear 111a and 111b.Two actuation gear 111a are connected on the live axle 102, so that they and the whole together rotation of live axle 102, and two driven gear 111b are supported by driven shaft 103.
When live axle 102 rotation, be connected in these two actuation gear 111a on 102 and all rotate.When actuation gear 111a rotates,, rotate along with the rotation of actuation gear 111a by driven shaft 103 corresponding driven gear 111b that support and that be meshed with actuation gear 111a.Therefore, pump chamber 111c special delivery fluid, thereby the pressure of raising fluid.
In the said gear pump, each end of live axle 102 and driven shaft 103 is all supported by bearing 104.Because this supporting structure near the position of gear 111a and 111b, all has the gap around each periphery of 102 and 103 in pump portion 101, promptly the inner space 105.Therefore, the problem this will occur from pump chamber 111c leak fluid to inner space 105, thus will reduce the efficient of gear pump
Here be useful on liquid gas fuel with for example dimethyl ether (after this being abbreviated as DME) and supply to fuel supply system in the car combustion engine.This fuel supply system is used the said gear pump sometimes.Gear pump does not have the impact of expansion.Therefore, gear pump has superiority when the DME that processing is easy to evaporate.
DME has lower viscosity, thereby it is easy to leak.Therefore, the fluid that leaks into the inner space 105 from above-mentioned pump chamber 111c is that DME will bring a series of problems.The gear pump that is installed on the automobile need have less size especially.Therefore, on the warp of the leakage road between pump chamber 111c and the inner space 105, be difficult to be provided with Sealing.
[summary of the invention]
The purpose of this invention is to provide a kind of gear pump, wherein it can reduce the fluid that leaks into the inner space from pump chamber.
In order to realize above-mentioned purpose, the invention provides a kind of gear pump that is used under pressure, transmitting fluid.This gear pump comprises the pump portion that sucks fluid and discharge pressure fluid.Pump portion comprises gear train, live axle and driven shaft.Gear train has the gear of pair of meshing.Each gear is determined a plurality of pump chambers that are used for transmitting in pump portion fluid.Live axle has periphery, and one of them gear engagement is on live axle, thus the whole together rotation of this gear and live axle.Driven shaft has periphery.Driven shaft supports another gear.Pump portion has the inner space, and it is located at the position that is adjacent at least one gear, and with respect at least one the periphery setting in live axle and the driven shaft.Pressed gas in the inner space is an intermediate-pressure gas, the pressure of its pressure fluid in being drawn into pump portion and discharging from pump portion between the pressure of fluid.
In conjunction with the drawings with the formal specification of example principle of the present invention, other aspects of the present invention and superiority will present from following explanation.
[description of drawings]
Below by in conjunction with the accompanying drawings and with reference to the explanation of currently preferred embodiment, with purpose and the superiority thereof that the present invention may be better understood.
Fig. 1 is the sectional view according to the pump of first embodiment of the invention;
Figure 1A is the zoomed-in view that is surrounded the zone by dot and dash line 1A among Fig. 1;
Fig. 2 is the sectional view along II-II line among Fig. 1;
Fig. 3 is the sectional view along III-III line among Fig. 1;
Fig. 4 provides the schematic representation of the fuel supply system of pump among Fig. 1;
Fig. 5 is the amplification view according to the substantial section of the pump of second embodiment of the invention;
Fig. 6 is the sectional view according to the pump of third embodiment of the invention;
Fig. 7 is the sectional view according to the pump of four embodiment of the invention;
Fig. 8 is the sectional view according to the pump of fifth embodiment of the invention; And
Fig. 9 is the sectional view of prior art pump.
[embodiment]
Various details first to the 5th embodiment.In second to the 5th embodiment, only explained and first embodiment's difference that promptly identical reference number is used to represent element identical or that be equal to, and has omitted the explanation to them.
As shown in Figure 4, fuel supply system has two-stage gear pump 1.Fuel supply system supplies fuel to and is used for driving the internal-combustion engine (motor) of automobile as driving source.The suction side of pump 1 is connected on the fuel tank 2 by suction pipe 3.Fuel tank 2 storages are as the DME (dimethyl ether) of fluid or liquid gas fuel.The discharge side of pump 1 is connected on the jet pump 5 by discharge tube 4.Motor 6 is connected on the discharge side of jet pump 5.Jet pump 5 is carried DME under the pressure of pump 1, it is supplied in the motor 6 with high pressure conditions.
As shown in Figure 1, pump 1 has pump case 7 and pump cover 9.Pump cover 9 is fixed in by a plurality of bolts 8 on the opening end that is essentially columniform pump case 7 bottoms, promptly on the left-hand end shown in Fig. 1.Pump case 7 and pump cover 9 constitute the pump chamber of pump 1.Pump 1 is that upper end and its right-hand side are that the state of lower end is installed on the automobile with left-hand side shown in Figure 1.Accommodate motor part 10 that is fixed on pump cover 9 internal surfaces and the pump portion 11 that is connected on the motor part 10 in the pump case 7.Thereby pump 1 and motor 10 are combined.In other words, pump 1 does not need external drive source, and the inside of pump 1 and outside seal separate.In pump case 7, the space outerpace of motor part 10 and pump portion 11 forms sub-fuel cavity 7a.In motor part 10 and pump portion 11, provide the rotating driveshaft 12 that passes these parts.
Motor part 10 has the columniform basically motor casing 10a in bottom.Motor part 10 comprises stator 10b and rotor 10c.Each stator 10b has the winding that is provided with along the inner circumferential surface of motor casing 10a.Rotor 10c is made of round the iron core of state setting stator 10b.In motor part 10, promptly in motor casing 10a, the space that holds stator 10b and rotor 10c constitutes motor cavity 60.Rotor 10c is fixed on the live axle 12, and and the whole together rotation of live axle 12.The winding of each stator 10b is connected on the terminal 15.When electric current when external power supply flows through the winding of stator 10b by terminal 15, live axle 12 rotates between the iron core of winding and rotor 10c under the electromagnetic induction effect.
Shown in Fig. 1 and 1A, pump portion 11 comprises matrix 16, connecting plate 19, side plate 20, connecting plate 21 and end plate 22, and arranges in proper order with this from motor part 10.Matrix 16 and plate 19-22 are by a plurality of through bolts 23 (seeing Fig. 2 and 3), and be fixing each other with the state that live axle 12 is inserted in wherein.Flange part 16a with matrix 16 is fixed on the motor casing 10a by a plurality of bolts 24 (only showing a bolt in Fig. 1), thereby pump portion 11 is fixed on the motor part 10.
Shown in Figure 1A, on live axle 12 part external peripheral surfaces, promptly near its lower end, be formed with groove 12a.Groove 12a extends along the axial direction of live axle 12.Key 25 with substantial rectangular cross section is arranged among the groove 12a.
Shown in Fig. 1 to 3, on live axle 12, provide first actuation gear 26 and second actuation gear 27, they are with the axial direction arrangement along live axle 12 from the lower end of this order.On the external peripheral surface of actuation gear 26 and 27, be formed with tooth 26a and 27a respectively.On the inner circumferential surface of actuation gear 26 and 27, be formed with keyway 26b and 27b respectively.By the surface that makes that key 25 engage splines 26b, 27b determine, thus make actuation gear 26 and 27 each all can with the whole together rotation of live axle 12.
In pump portion 11, accommodate the rotation driven shaft 29 that is parallel to live axle 12.Driven shaft 29 extends through matrix 16 that constitutes pump portion 11 and the plate 19-22 that constitutes pump portion 11.The upper end of driven shaft 29 (left-hand end shown in Fig. 1) is supported by matrix 16 by bearing 30.Be formed with groove 63 on the matrix 16.The upper end of driven shaft 29 and bearing 30 are located in the groove 63.The lower end of driven shaft 29 (right-hand member among Fig. 1) is supported by end plate 22 by bearing 31.Be formed with groove 64 on the end plate 22.The lower end of driven shaft 29 and bearing 31 are located in the groove 64.Bearing 30 and 31 each by constituting as the needle bearing of roller bearing.
On driven shaft 29, provide first driven gear 32 and second driven gear 33, they are with this 29 axial direction arrangement from lower end side along driven shaft in proper order.On the external peripheral surface of driven gear 32 and 33, be formed with tooth 32a and 33a respectively.Provide first driven gear 32 so that they can be with respect to driven shaft 29 rotations.Second driven gear 33 and driven shaft 29 integrally form.First driven gear 32 and corresponding first actuation gear 26 engagements on live axle 12, and second driven gear 33 and corresponding second actuation gear 27 engagements on live axle 12.
On the external peripheral surface of pump case 7, provide and suck joint 35.Suck joint 35 and have the suction port 35a that is communicated with sub-fuel cavity 7a, and be connected with the suction pipe 3 that extends out from fuel tank 2 (see figure 4)s.DME in fuel tank 2 imports by suction pipe 3 and suction port 35a, and is stored among the sub-fuel cavity 7a.When operating pumps portion 11, the DME that pump portion 11 sucks in sub-fuel cavity 7a.Pump portion 11 will increase the pressure of DME by a plurality of gear trains.Be that pump portion 11 is series connection forms.
Especially, pump portion 11 has first order gear train 36 and second level gear train 37, and first order gear train 36 i.e. first gear train or low voltage side gear train, and it is made of first actuation gear 26 and first driven gear 32; Second level gear train 37 is second gear trains that are made of second actuation gear 27 and second driven gear 33.First order gear train 36 is as the low voltage side gear train.Second level gear train 37 is as the high pressure side gear train.By making the DME Continuous Flow cross first order gear train 36 and second level gear train 37, pump portion 11 will progressively increase the pressure of DME.On the outer surface of pump cover 9, provide and discharge joint 39.Discharge joint 39 and have exhaust port 39a, and be connected with the discharge tube 4 that extends out from jet pump 5 (see figure 4)s.The DME that pump portion 11 has raise pressure is discharged to the discharge tube 4 from exhaust port 39a by the first pump portion inner passage (not shown).
As shown in Figure 2, connecting plate 21 has the hole 21b that is used to hold the hole 21a of first actuation gear 26 and is used to hold first driven gear 32.Connecting plate 21 has upstream passageway 40 and downstream passage 41.Owing to have upstream passageway 40 and downstream passage 41, connecting plate 21 has a plurality of spaces in the both sides of first actuation gear 26 and first driven gear, 32 engaging pieces.Upstream passageway 40 and downstream passage 41 are as the passage of DME.Upstream passageway 40 is connected with sub-fuel cavity 7a by the second pump portion inner passage (not shown).Though do not illustrate, connecting plate 19 also has hole, upstream passageway and downstream passage, and they are identical with downstream passage 41 with hole 21a and 21b, upstream passageway 40 in the connecting plate 21.
The direction rotation of live axle 12 black arrow in Fig. 2 is promptly rotated along clockwise direction.Driven shaft 29 by gear train 36 and 37 along with the rotation of live axle 12 is rotated.In other words, driven shaft 29 is the rotation of white arrow indicated direction in Fig. 2, promptly along rotation counterclockwise.When live axle 12 and driven shaft 29 rotations, the DME that has been sent in the pump portion 11 flow in the first order gear train 36 by upstream passageway 40.First order gear train 36 has a plurality of low pressure pump chamber 36a and 36b.The DME that arrives in the first order gear train 36 transmits towards downstream passage 41 by pump chamber 36a and 36b.Each pump chamber 36a is determined by the inner circumferential surface of two adjacent teeth 26a of first actuation gear 26 and hole 21a.Each pump chamber 36b is determined by the inner circumferential surface of two adjacent teeth 32a of first driven gear 32 and hole 21b.
As shown in Figure 3, side plate 20 has the hole 20b that is used to insert the hole 20a of live axle 12 and is used to insert driven shaft 29, these two hole 20a and 20b setting adjacent one another are.The diameter of hole 20a is arranged to the diameter greater than live axle 12.Thereby, between live axle 12 and hole 20a, provide the gap.The diameter of hole 20b is arranged to the diameter greater than driven shaft 29.Thereby, between driven shaft 29 and hole 20b, provide the gap.
Second level gear train 37 has a plurality of high pressure pump chamber 37a and 37b.Shown in Figure 1A, the DME that arrives in the second level gear train 37 is sent to exhaust port 39a by pump chamber 37a or 37b.Each pump chamber 37a be by two adjacent teeth 27a of second actuation gear 27 and in connecting plate 19 inner circumferential surface of respective aperture determine.Each pump chamber 37b be by two adjacent teeth 33a of second driven gear 33 and in connecting plate 19 inner circumferential surface of respective aperture determine.Be transported to the DME of exhaust port 39a, after increasing its pressure, supply in the jet pump 5 by discharge tube 4 by second level gear train 37.Be that pump portion 11 discharges the fluid that is drawn into wherein by pump chamber 36a to 37b from fluid communication passageways, wherein fluid communication passageways comprises pump chamber 36a to 37b.Pressure in the fluid communication passageways starting point is the suction pressure of pump portion 11, and is the head pressure of pump portion 11 at the pressure of fluid communication passageways end point.
Slide member in motor part 10 and the slide member in pump portion 11, for example gear 26,27,32 and 33, and they will produce heat when slide.Because the influence that is subjected to producing heat, DME in sub-fuel cavity 7a and the DME that leaks into the motor cavity 60 from gear train 36,37 can evaporate.In this embodiment, the inside of pump 1 and outside seal separate.In other words, the pump 1 of assembled motor 10 is shaft sealing types, and wherein live axle 12 is sealed in pump case 7 and the pump cover 9.In the pump 1 of shaft sealing type, vaporized DME may build up in sub-fuel cavity 7a or motor cavity 60.Yet, vaporized DME moves in the motor cavity 60 by exhaust port 57 in sub-fuel cavity 7a, and vaporized DME and gets back in the fuel tank 2 with this in proper order by inner space, leakage hole 56 and the blow-by tube 55 of intercommunicating pore 65, groove 61 in motor cavity 60.Therefore, can prevent from for example to cause the generation of the problem that motor part 10 can not fully cool off by being full of DME steam.
In pump portion 11, the periphery 12b that centers on live axle 12 has inner space 51 in the position of adjacency actuation gear 26 and 27.Inner space 51 comprises the first space 51a, the second space 51b and the 3rd space 51c.The first space 51a is located between first actuation gear 26 and the bearing 14.The first space 51a provides the part of the groove 62 in end plate 22.The second space 51b is located between actuation gear 26 and 27.The 3rd space 51c is located at the upside of second actuation gear 27.On live axle 12, from the middle part of matrix 16 to the diameter of live axle 12 lower end range sections less than its upper part diameter.The 3rd space 51c is located between this small diameter portion and matrix 16 of live axle 12 lower end side.
The first space 51a and the second space 51b are communicated with each other by some gaps around key 25 and keyway 12a.Similarly, the second space 51b and the 3rd space 51c are communicated with each other by some gaps around key 25 and keyway 12a.If necessary, the communication passage of the first space 51a and the second space 51b can be on first actuation gear 26, be formed for connecting, or the communication passage of the second space 51b and the 3rd space 51c can be on second actuation gear 27, be formed for connecting.
In the groove 62 of end plate 22, on the lower end surface of the live axle 12 that surpasses bearing 14, have space 62a.Space 62a is connected with the first space 51a by the gap that bearing 14 is had.Gap between the large-diameter portion of the 3rd space 51c by matrix 16 and live axle 12 divided, be that intercommunicating pore 67 is connected with motor cavity 60.As mentioned above, the inner space of motor cavity 10a further groove 61 is connected with motor cavity 60 by the intercommunicating pore on motor casing 10a 65.Especially, the space 61a that is positioned of the upper-end surface of live axle 12 is connected with motor cavity 60 by intercommunicating pore 65.
Therefore, the lower end surface that the upper-end surface of live axle 12 is positioned the pressed gas (pressure atmosphere) of space 61a and live axle 12 is positioned the pressed gas of space 62a, and they are identical with pressed gas in the motor cavity 60.Pressure in motor cavity 60 approximates the suction pressure of pump portion 11 greatly.Therefore, be applied to the power on live axle 12 upper-end surfaces based on pressure in the groove 61 and the power that is applied on live axle 12 lower end surfaces based on pressure in the groove 62 is mutual balance.Consequently, the relative promotion load that is applied on the live axle 12 owing to the imbalance of pressure in pressure in the groove 61 and the groove 62 will mutually offset, thereby reduce the promotion load of being born by bearing 13, and then improve the durability of bearing 13.
In addition, the pressed gas among the first space 51a is identical with the pressed gas of the second space 51b that is arranged in adjacency 51a place, first space, has first actuation gear 26 between them.Therefore, the relative promotion load that is applied on first actuation gear 26 owing to the imbalance of pressure in the first space 51a and pressure in the second space 51b will mutually offset.Consequently, the wearing and tearing and the other forms of damage of first actuation gear 26 have been prevented.Similarly, the pressed gas among the second space 51b is identical with the pressed gas of the 3rd space 51c that is arranged in adjacency 51b place, second space, has second actuation gear 27 between them.Therefore, be applied to relative promotion load on second actuation gear 27 with eliminating imbalance owing to pressure in the 3rd space 51c and pressure in the second space 51b each other.Consequently, the wearing and tearing and the other forms of damage of second actuation gear 27 have been prevented.
In pump portion 11, the periphery 29a that centers on driven shaft 29 has inner space 52 in the position of adjacency driven gear 32 and 33.Inner space 52 comprises the first space 52a, the second space 52b and the 3rd space 52c.The first space 52a is located between first driven gear 32 and the bearing 31.Promptly the first space 52a provides the part of the groove 64 in end plate 22.The second space 52b is located between driven gear 32 and 33.The 3rd space 52c is located between second driven gear 33 and the bearing 30.Promptly the 3rd space 52c provides the part of the groove 63 in matrix 16.
The first space 52a and the second space 52b are communicated with each other by some gaps between the periphery 29a of first driven gear 32 and driven shaft 29.In the groove 64 of end plate 22, on the lower end surface of driven shaft 29, have space 64a.Space 64a is connected with the first space 52a by the gap that bearing 31 is had.In the groove 63 of matrix 16, on the upper-end surface of driven shaft 29, have space 63a.Space 63a is connected with the 3rd space 52c by the gap that bearing 30 is had.In matrix 16, be in the space 63a of driven shaft 29 upper end surfaces,, be connected with the space 64a that in end plate 22, is in place, driven shaft 29 lower end surfaces by the interior axis channel 86 that in driven shaft 29, forms.Interior axis channel 66 extends along the axial direction of driven shaft 29.
Therefore, to be positioned the pressed gas of space 63a be identical with the pressed gas that the lower end surface of driven shaft 29 is positioned space 64a in the upper-end surface of driven shaft 29.Therefore, be applied to the power on driven shaft 29 upper-end surfaces based on pressure in the groove 63 and the power that is applied on driven shaft 29 lower end surfaces based on pressure in the groove 64 is mutual balance.Consequently, will eliminate owing to these two force unbalances are applied to promotion load on the driven shaft 29.In addition, the pressed gas among the second space 52b is identical with the pressed gas of the 3rd space 52c that is arranged in adjacency 52b place, second space, has second driven gear 33 between them.Therefore, to eliminate each other, and be applied to relative promotion load on second driven gear 33 owing to pressure in the second space 52b and the imbalance of pressure produces in the 3rd space 52c thrust and owing to pressure in groove 63 and the imbalance of pressure produces in groove 64 thrust.Consequently, the wearing and tearing and the other forms of damage of second driven gear 33 have been prevented.
In addition, the pressed gas among the first space 52a is identical with the pressed gas of the second space 52b that is arranged in adjacency 52a place, first space, has first driven gear 32 between them.Therefore, be applied to relative promotion load on first actuation gear 32 with eliminating imbalance owing to pressure in the first space 52a and pressure in the second space 52b each other.Consequently, the wearing and tearing and the other forms of damage of first driven gear 32 have been prevented.
In the head pressure that is used for the pressure that first order gear train 36 is communicated to the communication passage 43 on the second level gear train 37 is equaled first order gear train 36, in other words, i.e. the suction pressure of second level gear train 37.Especially, the pressure in communication passage 43 is higher than the suction pressure of first order gear train 36, i.e. the suction pressure of pump portion 11; And be lower than the head pressure of second level gear train 37, i.e. the head pressure of pump portion 11.In other words, to can be said to be the pressed gas that has intermediate pressure in the pump portion 11 to the pressed gas in the communication passage 43.In this embodiment, communication passage 43 is as the intermediate pressure zone.
Shown in Figure 1A and 3, side plate 20 has pressure introduction channel 67.In the position near driven shaft 29, pressure introduction channel 67 is connected to the first passage 43a of communication passage 43 among the second space 52b of inner space 52.Intermediate pressure in communication passage 43 imports among the second space 52b by pressure introduction channel 67.As mentioned above, the second space 52b is communicated in the inner space of the groove 64 in end plate 22, promptly is communicated among the first space 52a and the space 64a.The inner space of groove 64 is communicated to the 3rd space 52c.Therefore, pressed gas in the inner space of driven shaft 29 periphery 29a, be in the pressed gas among the space 63a of driven shaft 29 upper-end surfaces and be in pressed gas among the space 64a of driven shaft 29 lower end surfaces, all with communication passage 43 in pressed gas, be that to have the pressed gas of intermediate pressure in the pump portion 11 identical.
The embodiment who has said structure has following superiority.
(1) near the pressed gas in the inner space 52 of driven shaft 29 in the pump portion 11, be the pressed gas that has intermediate pressure in the pump portion 11.Therefore, for example when the suction pressure of the pressed gas of contrast in the inner space 52 and pump portion 11 or head pressure, when they are identical, reduced the maximum value of the pressure difference of generation between near pump chamber 36b, the 37b of driven shaft 29 and inner space 52.
Therefore, for example when the pressure of contrast in the inner space 52 equals the situation of suction pressure of pump portion 11, reduced the leakage rate that leaks into DME the inner space 52 from high pressure pump chamber 37b.In addition, for example when the pressure of contrast in the inner space 52 equals the situation of head pressure of pump portion 11, reduced the leakage rate that space 52 internally leaks into DME among the low pressure pump chamber 36b.Consequently, integrally improved the efficient of pump 1.
As mentioned above, owing to reduced the leakage rate of DME between near pump chamber 36b, the 37b of driven shaft 29 and inner space 52, and do not use Sealing, thus can make the pump 1 of reduced size.Therefore, this embodiment's pump 1 is applicable to and is installed on the automobile.
(2) according to this embodiment, in pump portion 11, inner space 52 is communicated in communication passage 43 as the intermediate pressure zone by pressure introduction channel 67.Therefore, by for example simple structure of pressure introduction channel 67, make inner passage 52 make pressed gas with intermediate pressure.
(3) be communicated with the communication passage 43 formation intermediate pressure zones of the discharge side of first order gear train 36 to the suction side of second level gear train 37.For example, when first order gear train 36 as the intermediate pressure zone under pressure in the transport process, during intermediate pressure among contrast low pressure pump chamber 36a, the 36b, the high pressure that first order gear train 36 is discharged imports in the inner space 52.Therefore, the maximum pressure differential that produces between pump chamber 36b, 37b and the inner space 52 will further be reduced in.Consequently, further improve the efficient of pump 1.
In addition, for example when transmitting under pressure in the process of impacting, when contrast intermediate pressure zone was arranged on the situation of pump chamber 36a, 36b, 37a, 37b, it was simple form that pressure introduction channel 67 is arranged to, and it is reducing to have superiority on pump 1 size.
As shown in Figure 5, in second embodiment, between matrix 16 and live axle 12, provide shaft sealer 71.Shaft sealer 71 makes motor cavity 60 not be connected with the 3rd space 51c of inner space 51 in the pump portion 11.Shaft sealer 71 comprises the Sealing of for example lip seal.Side plate 20 has pressure introduction channel 72.Pressure introduction channel 72 is communicated to the first passage 43a of communication passage 43 on the second space 51b of inner space 51.
Therefore, the intermediate pressure of communication passage 43 imports on the second space 51b of inner space 51 by pressure introduction channel 72.In other words, the pressed gas in the inner space 51 of the periphery 12b of live axle 12 and be in pressed gas among the space 62a at place, lower end surface of live axle 12, all with pump portion 11 in have an intermediate pressure pressed gas be identical.
Therefore in this embodiment, also can be reduced in the maximum pressure differential that produces near between pump chamber 36a, the 37a of live axle 12 and the inner space 51.Consequently, identical with above-mentioned first embodiment's situation at pump chamber 36a, 37a with the relation between the inner space 51 near live axle 12, promptly pump chamber 36b, the 37b with close driven shaft 29 is identical with the relation between the inner space 52, reduces the effect that DME leaks thereby reach.Because near pump chamber 36a, the 37a of live axle 12 and the relation between the inner space 51 and near pump chamber 36b, the 37b of driven shaft 29 and the relation between the inner space 52, in these two, all reduce the leakage of DME, thereby further improved the efficient of pump 1.
As shown in Figure 6, in the 3rd embodiment, exhaust port 57 in motor casing 10a and the pressure introduction channel 67 in side plate 20 from above-mentioned first embodiment, have been removed.In groove 63, be in the space 63a (seeing Figure 1A) of driven shaft 29 upper-end surfaces, be connected with motor cavity 60 by the intercommunicating pore 75 that passes matrix 16.The 3rd space 51c (seeing Figure 1A) of the inner space 51 of close live axle 12 is that intercommunicating pore 76 is connected with motor cavity 60 by the gap between dividing in the large-diameter portion of matrix 16 and live axle 12.Therefore, the pressed gas in the inner space 51 and 52 is identical with pressed gas in the motor cavity 60.
The point midway of leakage hole 56 in pipeline joint 54 is provided with pressure regulator valve 77.Pressure regulator valve 77 is the different pressures modulating valve that comprise valve member 77a and driving spring 77b.According to being applied to the pressure on the 77a in motor cavity 60 sides and being applied to pressure difference between the pressure on the valve member 77a equally in fuel tank 2 (see figure 4) sides, pressure regulator valve 77 can open and close leakage hole 56.
High pressure pump chamber 37a and 37b (seeing Figure 1A) are as the high-pressure area.Pressure in the high-pressure area is higher than the pressure in inner space 51 and 52.Because leakage, the leakage of pressure just of DME from pump chamber 37a and 37b, and the evaporation of DME in motor cavity 60, thereby improve pressure in inner space 51,52 and motor cavity 60.If becoming, the pressure in inner space 51,52 and motor cavity 60 is higher than predetermined value, the valve member 77a of pressure regulator valve 77 will overcome by driving spring 77b produce along the active force of valve closing direction and the active force that produces by the pressure that is connected in fuel tank 2 parts along the valve closing direction, open direction along valve and move.Therefore, valve member 77a discharges leakage hole 56.Thereby, by leakage hole 56 pressure is sent in the fuel tank 2, make that the pressure in inner space 51,52 and motor cavity 60 trends towards reducing, thereby pressure is got back to above-mentioned predetermined value.
In the state that leakage hole 56 is opened, if becoming, the pressure in inner space 51,52 and motor cavity 60 is lower than predetermined value, the valve member 77a of pressure regulator valve 77 will driving spring 77b under the active force of valve closing direction and by be connected to that pressure in fuel tank 2 parts produces under the active force of valve closing direction, move along the valve closing direction, thereby close leakage hole 56.Therefore, by leakage and the evaporation of DME, make that the pressure in inner space 51,52 and motor cavity 60 trends towards raising, thereby pressure is got back to above-mentioned predetermined value.
In other words, pressure regulator valve 77 automatically opens and closes leakage hole 56, so that the pressure in inner space 51,52 and motor cavity 60 remains on predetermined value.The structure proportion of independent pressure regulator valve 77 such as the pressure regulator valve of external control type simple in structure.Above-mentioned predetermined value, promptly the pressure of realizing by pressure regulator valve 77 in inner space 51,52 and motor cavity 60 is regulated target, be arranged in the intermediate pressure of pump portion 11 under the steady state operation condition, for example be arranged to the head pressure of first order gear train 36.It specifically is to realize by the spring force of regulating driving spring 77b that pressure is regulated being provided with of target.Therefore, under above-mentioned second embodiment's situation, inner space 51 and 52 has the pressed gas that has intermediate pressure in the pump portion 11.Therefore, reduced the leakage of DME between pump chamber 36a, 36b, 37a, 37b and respective inner space 51,52.
In this embodiment, by changing the operating characteristics of pressure regulator valve 77, the spring force of driving spring 77b for example can easily change the desired value of pressure in inner space 51 and 52.Therefore, by simple working, with the pressure corrections in inner space 51 and 52 different between pump and the pump to desirable numerical value.For example, in above-mentioned second embodiment,, need to change the diameter of pressure introduction channel 67 and 72 etc. in order to proofread and correct the different pressure in inner space 51 and 52 between pump and the pump.The work that changes diameter and other sizes like this is than trouble.In this embodiment, the correction of pressure comes easilier.
Pressure leakage from pump portion 11 is inevitable phenomenon.Pressure leakage makes the pressure in inner space 51 and 52 raise.In this embodiment, because pressure leakage is inevitably in the pump portion 11, therefore, make inner space 51 and 52 have intermediate-pressure gas by utilizing pressure trend of rising in inner space 51 and 52.Be not similar to second embodiment's pump 1, in this embodiment's pump 1, inner space 51 and 52 does not need to keep apart with motor cavity 60.In this embodiment's pump 1, inner space 51,52 and motor cavity 60 are communicated with each other, and for example the DME that leaks from second level gear train 37 must supply to the motor cavity 60 by inner space 51,51 and intercommunicating pore 75,76.Consequently, by supplying to the better cooling motor of the liquid DME portion 10 in the motor cavity 60.Thereby, keep the stable of motor part 10 operations.
In this embodiment, the inner space of intercommunicating pore 75 and 76, motor cavity 60, intercommunicating pore 65, groove 61, leakage hole 56 and leakage pipe 55 (see figure 4)s usefulness connect the fuel tank 2 of area of low pressure and the pressure regulator channel of inner space 51,52.
As shown in Figure 7, in pump 1, be that the pump 1 to above-mentioned the 3rd embodiment changes according to the 4th embodiment.Especially, the upstream side of the leakage hole 56 of pipeline joint 54 is communicated to the upper space of sub-fuel cavity 7a.Has the inner passage 79 that is used for the inner space of groove 61 is communicated to sub-fuel cavity 7a upper space in the pump cover 9.The DME of evaporation discharges by the inner space and the inner passage 79 of intercommunicating pore 65, groove 61 in motor cavity 60, and gets back to together in the fuel tank 2 by leakage hole 56 and leakage pipe 55 and the DME that evaporates in sub-fuel cavity 7a.
In inner passage 79, be provided with pressure regulator valve 77, by as above-mentioned the 3rd embodiment in same operation, being adjusted to intermediate pressure at the pressure in the motor cavity 60.In this embodiment, sub-fuel cavity 7a is as the area of low pressure.The inner space of intercommunicating pore 75 and 76, motor cavity 60, intercommunicating pore 65, groove 61 and inner passage 79 are as inner space 51,52 is communicated to the area of low pressure, is the pressure regulator channel of sub-fuel cavity 7a.
As shown in Figure 8, in the 5th embodiment, be that above-mentioned the 3rd embodiment changed.Especially, motor part 10 is arranged on the bottom (right-hand side shown in Fig. 8) of pump case 7, and pump portion 11 is arranged on the top (left-hand side shown in Fig. 8) of pump case 7.In other words, pump 1 with pump portion 11 at upper position and motor part 10 is installed on the automobile at the state of lower position.
By such structure, pump portion 11 and the discharge joint 39 that is installed on the pump cover 9 are arranged to form close to each other.Therefore, be provided for easily pump portion 11 is communicated to the first pump portion inner passage (not shown) of discharging joint 39, this has superiority on the size that reduces pump 1.In addition, because motor part 10 is arranged on the bottom of pump case 7, therefore guarantee that the liquid level of DME in motor cavity 60 is located at the top of motor cavity 60.Therefore, stator 10b and rotor 10c be less may be in the DME liquid level above, thereby can cool off them better by DME (liquid).
In this embodiment, the upstream side of leakage hole 56 is communicated in the inner space of end plate 22 further groove 62.Leakage hole 56 and motor cavity are communicated with each other by inner space 51 and the intercommunicating pore 76 near live axle 12.Therefore, the DME of evaporation is discharged in the fuel tank 2 by intercommunicating pore 76, inner space 51, leakage hole 56 and leakage pipe 55 (see figure 4)s in motor cavity 60.
Under the influence that DME leaks from as the high pressure pump chamber 37a of high-pressure area and 37b (seeing Figure 1A), and DME is in motor cavity 60 under the influence of evaporation, and the pressure in inner space 51 trends towards rising.On the other hand, the pressure in inner space 51 is discharged in the fuel tank 2 by leakage hole 56 and leakage pipe 55.By regulating the openings of sizes of drain port 56, and regulate the degree that discharges pressure in the space 51 internally, thereby pressure regulator valve 77 will be adjusted to the intermediate pressure of pump portion 11 at the pressure in the inner space 51.
In this embodiment, omitted intercommunicating pore 75.In other words, the inner space 52 near driven shaft 29 keeps apart with motor cavity 60.Yet inner space 52 is communicated on the communication passage 43 between gear train 36 and 37 by pressure introduction channel 67.In other words, by as above-mentioned first embodiment in identical method, make to make to have the pressed gas that has intermediate pressure in the pump portion 11 near the inner space 52 of driven shaft 29.
In this embodiment, be directly to regulate near the pressure in the inner space 51 of live axle 12 by pressure regulator valve 77.On the contrary, for example in above-mentioned the 3rd embodiment, the pressure in motor cavity 60 is directly to regulate, and in motor cavity 60 on the pressure of the pressure feedback after the combination in the inner space 51.In this embodiment, therefore when contrasting with above-mentioned the 3rd embodiment, the operation of pressure regulator valve 77 feeds back on the pressure of inner space 51 immediately.Therefore, will make that the pressure in inner space 51 is further stable.Consequently, the leakage of DME between low pressure pump chamber 36a, high pressure pump chamber 37a and the close inner space 51 of live axle 12 will more effectively be suppressed at.
In this embodiment, the inner space of groove 62, leakage hole 56 and leakage pipe 55 (see figure 4)s are as the pressure regulator channel that is communicated with inner space 51 and fuel tank 2.
The present invention can implement with following form.
By changing above-mentioned first or second embodiment, in first order gear train 36 or second level gear train 37, pump chamber 36a, 36b, 37a, 37b under pressure in the transport process as the intermediate pressure zone.Especially, in the situation that first embodiment revises, inner space 51 is communicated in the intermediate pressure zone by the pressure introduction channel.In the situation that second embodiment revises, inner space 51 and 52 is communicated in the intermediate pressure zone by the pressure introduction channel.
In above-mentioned second embodiment, omitted pressure introduction channel 67.In other words, have only inner space 51 to make and have intermediate pressure.
In above-mentioned the 3rd to the 5th embodiment, pressure regulator valve 77 is independent (pressure-difference valves).By changing this valve, for example using, the external control type valve of solenoid valve is used as pressure controlled valve.In this case, in the 5th embodiment's modification, provide pressure transducer and control gear (the following describes) at the 3rd.Pressure transducer detects the pressure in respective inner space 51 and 52, or detection and described space have the pressure in the space of uniform pressure gas.For example the control gear of computer is according to the detection information that sends from pressure transducer, the opening and closing of pilot pressure control valve.Therefore, can open and close the pressure regulator channel that is communicated with inner space 51,52 and area of low pressure according to the pressure in the side of area of low pressure, respective inner space.Therefore, can guarantee the pressure in respective inner space 51 and 52 is adjusted to and have predetermined value.
In the above-described embodiments, the present invention implements with the pump 1 that for example is installed in fuel tank 2 outside forms.By changing this form, the present invention can implement with the gear pump that is called the fuel tank inner, and the pump of this kind form is included in the inside of fuel tank 2.In this case, can omit pump case 7.
Being not limited only to by the fluid of gear pump operation is DME.The present invention can implement with the gear pump that operation is different from the liquid (gas) of DME.
In the above-described embodiments, the present invention implements with the two-stage gear pump.Yet the present invention is not limited only to the gear pump of this form.The present invention can implement with the multi-stage gear pump that is different from two-stage, for example three grades or level Four gear pump.Selectively, the present invention can implement with the one-level gear.
In the above-described embodiments, gear pump is the shaft sealing type, i.e. motor combination form therein.Yet gear pump can be that axle is opening, promptly by the form of external motors driven pump portion.
Be not limited only under pressure, liquid gas fuel is transported to the automobile gear pump of internal-combustion engine according to gear pump of the present invention.The present invention can be applied to for example gear pump that is used for delivering hydraulic fluid etc. under pressure in machine tool.
It is illustrative that these examples and embodiment should be considered to, rather than determinate, and the present invention is not limited only to details given here, but can make amendment in the scope of accessory claim and equivalents.
Claims (12)
1. gear pump that is used under pressure transmitting fluid, this gear pump comprises a pump portion that sucks fluid and discharge pressure fluid, and wherein this pump portion comprises:
Gear train with pair of engaged gears, wherein each gear is determined a plurality of pump chambers that are used for transmitting in pump portion fluid;
Live axle with periphery, one of them gear engagement are on live axle, thus the whole together rotation of this gear and live axle; And
Have a driven shaft of periphery, wherein this driven shaft supports another gear, and this pump is characterised in that:
Pump portion has an inner space, it is located at the position that is adjacent at least one gear, and with respect at least one the periphery setting in live axle and the driven shaft, and wherein the pressed gas of this inner space is an intermediate-pressure gas, the pressure of its pressure fluid in being drawn into pump portion and discharging from pump portion between the pressure of fluid.
2. gear pump as claimed in claim 1, it is characterized in that, pump portion has a fluid communication passageways that comprises pump chamber, wherein pump portion discharges the fluid that is drawn into wherein by pump chamber from fluid communication passageways, wherein this fluid communication passageways has an intermediate pressure zone, the pressure of pressed gas is the intermediate pressure between the pressure of fluid in being drawn into fluid communication passageways and the pressure of discharging fluid from fluid communication passageways in this zone, and wherein pump portion has a pressure introduction channel, and it is connected the inner space with the intermediate pressure zone.
3. gear pump as claimed in claim 2, it is characterized in that, described gear train is in a plurality of gear trains, a plurality of gear trains comprise at least one first gear train and one second gear train, wherein fluid communication passageways comprises a communication passage, be used to guide fluid to be discharged to second gear train, and wherein this communication passage is used as the intermediate pressure zone from first gear train.
4. gear pump as claimed in claim 1, it is characterized in that also comprising a pressure regulator valve, this pressure regulator valve can discharge the pressure of inner space, thereby the pressure of inner space is adjusted to an intermediate pressure, the pressure of this pressure fluid in being drawn into pump portion and from pump portion, discharging between the pressure of fluid.
5. gear pump as claimed in claim 4, it is characterized in that, pump portion has a fluid communication passageways that comprises pump chamber, wherein pump portion discharges the fluid that is drawn into wherein by pump chamber from fluid communication passageways, wherein this fluid communication passageways has a high-pressure area, internal pressure in this zone is higher than the pressure of inner space, and wherein said pressure regulator valve prevents that the pressure of inner space is owing to pressure leaks into the rising that causes the inner space from the high-pressure area.
6. gear pump as claimed in claim 4 is characterized in that the inner space is communicated on the hopper by a pressure regulator channel, and the hopper storage supplies to the fluid in the pump portion, and wherein pressure regulator valve is located in this pressure regulator channel.
7. gear pump as claimed in claim 6 is characterized in that comprising,
Be used to hold a housing of pump portion; And
One sub-hopper, wherein this sub-hopper is stored in housing from hopper and to be supplied with the fluid of coming, so that this fluid is supplied in the pump portion,
Wherein this sub-hopper is provided in the part that is located at the pressure regulator channel between pressure regulator valve and the hopper.
8. gear pump as claimed in claim 6 is characterized in that also comprising,
A motor that is used for rotating driveshaft; And
Be used to hold a housing of pump portion and motor,
Wherein pump portion has a gear housing that is used to hold gear, and
Wherein pump portion is located between pressure regulator valve and the motor, and wherein the gear housing has a passage that is used to be communicated with inner space and pressure regulator valve.
9. as any one described gear pump in the claim 1 to 7, it is characterized in that comprising,
A motor that is used for rotating driveshaft; And
Be used to hold a housing of pump portion and motor.
10. as any one described gear pump in the claim 1 to 7, it is characterized in that, the inner space is in a pair of inner space, this a pair of inner space is respectively to be determined by the periphery of the periphery of live axle and driven shaft, and wherein the pressed gas of each inner space is an intermediate-pressure gas, the pressure of its pressure fluid in being drawn into pump portion and discharging from pump portion between the pressure of fluid.
11., it is characterized in that fluid is a liquid gas fuel as any one described gear pump in the claim 1 to 7.
12., it is characterized in that gear pump is mounted on the automobile as any one described gear pump in the claim 1 to 7.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP69529/03 | 2003-03-14 | ||
| JP69529/2003 | 2003-03-14 | ||
| JP2003069529A JP2004278381A (en) | 2003-03-14 | 2003-03-14 | Gear pump |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN1534195A true CN1534195A (en) | 2004-10-06 |
| CN1299002C CN1299002C (en) | 2007-02-07 |
Family
ID=32767976
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CNB2004100352327A Expired - Fee Related CN1299002C (en) | 2003-03-14 | 2004-03-12 | Gear pump |
Country Status (4)
| Country | Link |
|---|---|
| US (1) | US20040179953A1 (en) |
| EP (1) | EP1457678A1 (en) |
| JP (1) | JP2004278381A (en) |
| CN (1) | CN1299002C (en) |
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103620221A (en) * | 2011-12-28 | 2014-03-05 | 萱场工业株式会社 | Electric oil pump |
| CN105378238A (en) * | 2013-02-27 | 2016-03-02 | C·C·詹森有限公司 | Device for processing a liquid under vacuum pressure |
| CN103802299B (en) * | 2012-11-02 | 2017-07-18 | 住友橡胶工业株式会社 | The manufacture method of gear pump extruder and the extrusion gear used in the extruder |
| CN110073095A (en) * | 2016-12-12 | 2019-07-30 | 罗伯特·博世有限公司 | Electric gear wheel pump |
| CN110100099A (en) * | 2016-12-22 | 2019-08-06 | 罗伯特·博世有限公司 | Electric gear wheel pump |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US20070201989A1 (en) * | 2005-10-14 | 2007-08-30 | Parker-Hannifin | Low ripple gear pump/motor |
| JP4678324B2 (en) * | 2006-04-10 | 2011-04-27 | 株式会社豊田自動織機 | Electric pump |
| JP2007315238A (en) * | 2006-05-24 | 2007-12-06 | Toyota Industries Corp | Gear pump |
| US20100266437A1 (en) * | 2009-04-16 | 2010-10-21 | Argo-Tech Corporation | Aircraft main engine fuel pump with multiple gear stages using shared journals |
| US9611847B2 (en) | 2009-04-16 | 2017-04-04 | Eaton Industrial Corporation | Aircraft main engine fuel pump with multiple gear stages using shared journals |
| US9032840B2 (en) * | 2010-04-07 | 2015-05-19 | Gm Global Technology Operations, Llc | Evacuated transmission case |
| JP5767996B2 (en) * | 2012-03-29 | 2015-08-26 | カヤバ工業株式会社 | Fluid pressure drive unit |
| JP5934543B2 (en) * | 2012-03-29 | 2016-06-15 | Ｋｙｂ株式会社 | Fluid pressure drive unit |
| DE102015117562A1 (en) | 2014-10-16 | 2016-04-21 | Johnson Electric S.A. | gear pump |
| CN104361261B (en) * | 2014-12-08 | 2017-03-29 | 中国人民解放军防化学院 | A kind of gear pump health state evaluation method theoretical based on profust reliability |
| JP6348092B2 (en) * | 2015-10-29 | 2018-06-27 | 株式会社Ｓｏｋｅｎ | External gear type fuel pump |
| US9902251B2 (en) * | 2016-01-26 | 2018-02-27 | Deere & Company | Recess-mounted hydraulic pump cartridge and work vehicle drivetrain therewith |
| IT201600123972A1 (en) * | 2016-12-06 | 2018-06-06 | Bosch Gmbh Robert | GEAR ELECTRIC PUMP |
| IT201600129613A1 (en) * | 2016-12-21 | 2018-06-21 | Bosch Gmbh Robert | GEAR ELECTRIC PUMP |
| EP3724484A1 (en) * | 2017-12-13 | 2020-10-21 | Robert Bosch GmbH | Pumping unit for feeding fuel, preferably diesel fuel, to an internal combustion engine |
| CN109185124A (en) * | 2018-11-27 | 2019-01-11 | 沈阳航天新光集团有限公司 | A kind of integrated gear pump |
| DE102021116160A1 (en) * | 2021-06-22 | 2022-12-22 | Fte Automotive Gmbh | Gear pump and prime mover |
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| GB643931A (en) * | 1948-05-19 | 1950-09-27 | Aerostyle Ltd | Improvements in and relating to gear pumps, fluid motors and the like |
| DE1293599B (en) * | 1958-01-14 | 1969-04-24 | Borg Warner | Gear pump |
| GB8513684D0 (en) * | 1985-05-30 | 1985-07-03 | Boc Group Plc | Mechanical pumps |
| JPH0914154A (en) * | 1995-06-26 | 1997-01-14 | Shimadzu Corp | Gear pump or motor |
| JP3932595B2 (en) * | 1997-03-12 | 2007-06-20 | 株式会社日立製作所 | Gear pump |
| JP3688535B2 (en) * | 1999-11-17 | 2005-08-31 | 上田鉄工株式会社 | Gear pump |
| US6733249B2 (en) * | 2001-05-17 | 2004-05-11 | Delphi Technologies, Inc. | Multi-stage internal gear fuel pump |
-
2003
- 2003-03-14 JP JP2003069529A patent/JP2004278381A/en active Pending
-
2004
- 2004-03-10 US US10/798,136 patent/US20040179953A1/en not_active Abandoned
- 2004-03-11 EP EP04005946A patent/EP1457678A1/en not_active Withdrawn
- 2004-03-12 CN CNB2004100352327A patent/CN1299002C/en not_active Expired - Fee Related
Cited By (11)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103620221A (en) * | 2011-12-28 | 2014-03-05 | 萱场工业株式会社 | Electric oil pump |
| CN103620221B (en) * | 2011-12-28 | 2016-03-30 | Ｋｙｂ株式会社 | Electric oil pump |
| US9581159B2 (en) | 2011-12-28 | 2017-02-28 | Kyb Corporation | Electric oil pump |
| CN103802299B (en) * | 2012-11-02 | 2017-07-18 | 住友橡胶工业株式会社 | The manufacture method of gear pump extruder and the extrusion gear used in the extruder |
| CN105378238A (en) * | 2013-02-27 | 2016-03-02 | C·C·詹森有限公司 | Device for processing a liquid under vacuum pressure |
| CN105378238B (en) * | 2013-02-27 | 2018-01-16 | C·C·詹森有限公司 | Device for treatment liquid under the vacuum pressures |
| US10905973B2 (en) | 2013-02-27 | 2021-02-02 | C.C. Jensen A/S | Device for processing a liquid under vacuum pressure |
| CN110073095A (en) * | 2016-12-12 | 2019-07-30 | 罗伯特·博世有限公司 | Electric gear wheel pump |
| US11085441B2 (en) | 2016-12-12 | 2021-08-10 | Robert Bosch Gmbh | Electric gear pump |
| CN110073095B (en) * | 2016-12-12 | 2021-08-31 | 罗伯特·博世有限公司 | Electric gear pump |
| CN110100099A (en) * | 2016-12-22 | 2019-08-06 | 罗伯特·博世有限公司 | Electric gear wheel pump |
Also Published As
| Publication number | Publication date |
|---|---|
| EP1457678A1 (en) | 2004-09-15 |
| CN1299002C (en) | 2007-02-07 |
| US20040179953A1 (en) | 2004-09-16 |
| JP2004278381A (en) | 2004-10-07 |
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Granted publication date: 20070207 Termination date: 20100312 |