CN101251108A - Oil pump pressure control device - Google Patents
Oil pump pressure control device Download PDFInfo
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- CN101251108A CN101251108A CNA2008100092597A CN200810009259A CN101251108A CN 101251108 A CN101251108 A CN 101251108A CN A2008100092597 A CNA2008100092597 A CN A2008100092597A CN 200810009259 A CN200810009259 A CN 200810009259A CN 101251108 A CN101251108 A CN 101251108A
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- drain passageway
- side rotor
- return path
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- 239000003921 oil Substances 0.000 description 41
- 238000007789 sealing Methods 0.000 description 10
- 238000007599 discharging Methods 0.000 description 7
- 230000007246 mechanism Effects 0.000 description 6
- 238000010587 phase diagram Methods 0.000 description 6
- 230000002411 adverse Effects 0.000 description 5
- 238000010586 diagram Methods 0.000 description 5
- 230000000694 effects Effects 0.000 description 5
- 239000010705 motor oil Substances 0.000 description 4
- 230000009467 reduction Effects 0.000 description 4
- 230000008859 change Effects 0.000 description 3
- 230000007423 decrease Effects 0.000 description 3
- 238000000034 method Methods 0.000 description 3
- 230000000630 rising effect Effects 0.000 description 3
- 230000008901 benefit Effects 0.000 description 2
- 230000006835 compression Effects 0.000 description 2
- 238000007906 compression Methods 0.000 description 2
- 239000000446 fuel Substances 0.000 description 2
- 230000001052 transient effect Effects 0.000 description 2
- 230000009471 action Effects 0.000 description 1
- 230000015572 biosynthetic process Effects 0.000 description 1
- 230000010349 pulsation Effects 0.000 description 1
- 230000001105 regulatory effect Effects 0.000 description 1
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C14/00—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations
- F04C14/24—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by using valves controlling pressure or flow rate, e.g. discharge valves or unloading valves
- F04C14/26—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by using valves controlling pressure or flow rate, e.g. discharge valves or unloading valves using bypass channels
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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
- F04C14/00—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations
- F04C14/06—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations specially adapted for stopping, starting, idling or no-load operation
- F04C14/065—Capacity control using a multiplicity of units or pumping capacities, e.g. multiple chambers, individually switchable or controllable
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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
- F04C2/10—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Rotary Pumps (AREA)
- Details And Applications Of Rotary Liquid Pumps (AREA)
Abstract
The invention provides a flow quantity variable oil pump having two discharge ports and using three rotors. The inventive oil pump maintains pressure property same with that of normal oil pumps and reduces friction at the same time. The inventive oil pump comprises a first discharge passage (11) for supply oil to the engine; a return passage (E) that returns to an intake side of an outer circumferential side rotor (A); a second discharge passage (13) for supplying oil to the engine; a return passage (E) that returns to an intake side of an inner circumferential side rotor (B); and a pressure control valve whose valve main body is provided between a discharge port from the inner circumferential side rotor and the first discharge passage. The first and second discharge passage are coupled, and a flow passage control is executed in each of: a low revolution range in a state in which only the first and the second discharge passage are open; an intermediate revolution range in a state in which the first and second discharge passage are open and a first intake side of the return passage is closed while a second intake side of the return passage is open; and a high revolution range in a state in which the second discharge passage is closed while the first discharge passage and the return passage are open.
Description
Technical field
The present invention relates to a kind of pressure control device of oil pump, have two exhaust ports and as providing these two to discharge the mechanism in sources and use in the oil pump of changeable flow type of three rotors, by improving the oil circuit switching method to make pressure (oil pressure) characteristic not being the multistage characteristic but keep the identical characteristic of Pressure characteristics with general oil pump, the while can be reduced friction.
Background technique
In the past, by patent documentation 1, known three rotors self that conduct is arranged to the mechanism of two place's transferring oils.In patent documentation 1, only represented mechanism to two place's transferring oils, the effect outside this is not shown.
(patent documentation 1) Japanese kokai publication hei 11-280666
(patent documentation 2) TOHKEMY 2005-140022
(patent documentation 3) TOHKEMY 2002-70756
In a single day in the patent documentation 1,, determined by profile of tooth owing to just make, so flow-rate ratio is all much the same under which kind of rotating speed for the flow of inboard rotor and outside rotors.Especially,, might between inboard interdental spaces and outside interdental spaces, produce pressure difference, push center roller to a side, and quicken the wearing and tearing of the flank of tooth according to the parameter of inboard profile of tooth and outside profile of tooth.That is,, the significant drawback of center roller generation uneven wear is arranged owing to pressure difference.
In the patent documentation 2, by the rotary speed area in expectation oil release is reduced idle work, the efficient of pursuing under this rotary speed area improves.With reference to its Fig. 8 of the 13rd page, descend by the discharge capacity in the rotary speed area that makes expectation, reduce idle work and raise the efficiency.According to such changeable flow oil pump, can raise the efficiency, but have following problem.
Because the exhaust port of a group rotor is divided into two-part, so each opening area of discharging stream diminishes, have to increase root diameter in order to remedy this point, big if root diameter becomes, then friction (moment) becomes big, the shortcoming that exists efficient to reduce.In addition, improve, the problem that efficient reduces can occur although taked the variable capacity mode to pursue efficient in order to eliminate idle work.And then, owing to only the exhaust port of a group rotor is divided into two-part,, on the degrees of freedom of the distribution ratio of two discharge capacitys, there is restriction so the rotor parameter of two exhaust ports is identical certainly.This is owing to there are certain design constraints in a mouthful position, opening area.In addition,, overlap, thereby also have noise, vibration coincidence and become big shortcoming so discharge the opportunity of pulsation because two discharge sources discharge from same rotor.In addition, because rotor is 1 group, so, also do not reduce the shortcoming of the mechanism of this idle work in the rotor even if also there is the generation idle work.
Summary of the invention
Therefore, the problem to be solved in the present invention (technical problem or purpose etc.) is, the oil pump of three rotors of a kind of use is provided, it is a changeable flow type oil pump, have two exhaust ports and use three rotors as the mechanism that provides these two to discharge the source, by improving the oil circuit switching method, and make pressure (oil pressure) characteristic is not multistage characteristic and keep Pressure characteristics with general oil pump (in patent documentation 3, be the characteristic of its non-stage by a dotted line shown in Figure 10 of the 7th page, valve only has the function that discharges ON, OFF.In addition, the pole-changing of characteristic point is roughly one) identical characteristic, can reduce friction simultaneously.
Therefore, the present inventor is research with keen determination in order to solve above-mentioned problem, the result, and the invention of technological scheme 1 is a kind of pressure control device of oil pump, it is characterized in that, comprising: the oil pump that three rotors are arranged that possesses outer circumferential side rotor and interior all side rotors; From 1st drain passageway of above-mentioned outer circumferential side rotor to engine oil; Turn back to the return path of the suction side of above-mentioned outer circumferential side rotor; From 2nd drain passageway of above-mentioned interior all side rotors to engine oil; Turn back to the above-mentioned return path of the suction side of above-mentioned interior all side rotors; And the pressure controlled valve that in above-mentioned, is provided with valve body between the exhaust port of all side rotors and above-mentioned the 1st drain passageway, above-mentioned the 1st drain passageway and above-mentioned the 2nd drain passageway link, in low rotation speed area, with the State Control stream of the 1st drain passageway and the 2nd drain passageway opening only, in the medium speed zone, the State Control stream of the 2nd inlet side opening of above-mentioned return path with the 1st inlet side sealing of the 1st drain passageway and the 2nd drain passageway opening and above-mentioned return path, in high rotary speed area, the State Control stream of the 1st drain passageway opening and above-mentioned return path opening addresses the above problem thus with the sealing of the 2nd drain passageway.
In addition, the invention of technological scheme 2 is pressure control devices of a kind of oil pump, it is characterized in that, comprising: the oil pump that three rotors are arranged that possesses outer circumferential side rotor and interior all side rotors; From 1st drain passageway of above-mentioned outer circumferential side rotor to engine oil; Turn back to the 1st return path of the suction side of above-mentioned outer circumferential side rotor; From 2nd drain passageway of above-mentioned interior all side rotors to engine oil; Turn back to the 2nd return path of the suction side of above-mentioned interior all side rotors; And the pressure controlled valve that in above-mentioned, is provided with valve body between the exhaust port of all side rotors and above-mentioned the 1st drain passageway, the tip side of above-mentioned the 1st drain passageway and above-mentioned the 2nd drain passageway links, in low rotation speed area, with the State Control stream of the 1st drain passageway and the 2nd drain passageway opening only, in the medium speed zone, with the 1st drain passageway and the 2nd drain passageway opening and the sealing of above-mentioned the 1st return path and the State Control stream of the 2nd return path opening, in high rotary speed area, the State Control stream of the 1st drain passageway opening and the 1st return path and the 2nd return path opening addresses the above problem thus with the sealing of the 2nd drain passageway.
The invention of technological scheme 3 is pressure control devices of a kind of oil pump, in such scheme, it is characterized in that, above-mentioned pressure controlled valve is the type with the 1st valve portion and the 2nd valve portion, addresses the above problem thus.
In addition, the invention of technological scheme 4 is pressure control devices of a kind of oil pump, in such scheme, it is characterized in that, above-mentioned pressure controlled valve is the type with the 1st valve portion and the 2nd valve portion and the 3rd valve portion, addresses the above problem thus.
Invention according to technological scheme 1, particularly in the changeable flow type oil pump that uses three rotors, has following great advantage: can utilize other the drain passageway and the existence of return path and eliminate pressure difference by the pressure ratio of design phase decision, and the center roller of all side rotors can not pressed to a thruster in constituting, can prevent the wearing and tearing of its flank of tooth, improve durability.And then, when outer circumferential side rotor and the rotation of interior all side rotor high-speed, become independent loop thereby the 2nd drain passageway of interior all side rotors is closed interior all side rotors fully, do not make interior all side rotors produce useless working pressure, the effect that the pump integral pressure also can not descend even if having.In addition, owing to merit=pressure * flow, thus if descending, pressure then can reduce idle work, and because the not connection of the pump (auxiliary pump) of the pump (main pump) of outer circumferential side rotor and interior all side rotors, so can reduce the pressure of auxiliary pump significantly.
In addition, because the pump (auxiliary pump) of interior all side rotors is an independent loop when high rotating speed, so as long as increase the return path opening area of this pump, then oil just can be discharged better, the pressure of this pump is lower.Because these two discharge sources are not an exhaust port is cut apart but can be respectively to be set up as an exhaust port, so there be not cutting apart of flow.Therefore, compare with a common group rotor, the diameter of three rotors can reduce, and can reduce the slide area of rotor, so friction (moment) diminishes, can improve pump efficiency.And then, because if three rotors are formed by two group rotors as rotor, so also have the advantage of the idle work that can reduce the folk prescription rotor.In the invention of technological scheme 2, can play the effect identical with the invention of technological scheme 1.
In addition, in the invention of technological scheme 3, can not only play the effect identical, can also utilize the existence of simple control valve and reduce components number with the invention of technological scheme 1.In addition, in the invention of technological scheme 4, can utilize three valve-types pressure controlled valve existence and pressure control is the value of more approaching expectation.
Description of drawings
Fig. 1 is the system diagram of the 1st mode of execution of the present invention, is the phase diagram of the low rotation speed area of motor.
Fig. 2 is the system diagram of the 1st mode of execution of the present invention, is the phase diagram in the medium speed zone of motor.
Fig. 3 is the system diagram of the 1st mode of execution of the present invention, is the phase diagram of the high rotary speed area of motor.
Fig. 4 is the system diagram of the 2nd mode of execution of the present invention, is the phase diagram of the low rotation speed area of motor.
Fig. 5 is the local system figure of the 2nd mode of execution of the present invention, is the phase diagram in the medium speed zone of motor.
Fig. 6 is the local system figure of the 2nd mode of execution of the present invention, is the phase diagram of the high rotary speed area of motor.
Fig. 7 is a concise and to the point system diagram of the present invention.
Fig. 8 A is the property list of engine speed of the present invention and head pressure, and Fig. 8 B is the rotating speed of motor of the present invention and the property list of discharge flow rate.
Description of reference numerals
A ... the outer circumferential side rotor
B ... interior all side rotors
E ... motor
11 ... the 1st drain passageway
8,9 ... suck path
12 ... the 1st return path
13 ... the 2nd drain passageway
14 ... the 2nd return path
C ... pressure controlled valve
21 ... the 1st valve portion
22 ... the 2nd valve portion
24 ... the 3rd valve portion
Embodiment
Below, embodiments of the present invention are described with reference to the accompanying drawings, shown in each figure is the oil pump of triple-spool type, mainly comprises external rotor 1 and center roller 2 and inner rotator 3.At said external rotor 1 and above-mentioned center roller 2 places outer circumferential side suction port 4 and outer circumferential side exhaust port 5 are set, all side draught inlets 6 and interior all side exhaust ports 7 in above-mentioned center roller 2 is provided with above-mentioned inner rotator 3 places.Said external rotor 1 and above-mentioned center roller 2 and outer circumferential side suction port 4 and interior all side draught inlets 5 are generically and collectively referred to as the outer circumferential side rotor, all side rotors in above-mentioned center roller 2 and above-mentioned inner rotator 3 and interior all side draught inlets 6 and interior all side exhaust ports 7 are generically and collectively referred to as.
In the oil pump of triple-spool type, comprise from above-mentioned outer circumferential side exhaust port 5 to the 1st drain passageway 11 of motor E fuel feeding, turn back to the 1st return path 12 of the suction path 8 of above-mentioned outer circumferential side suction port 4, in above-mentioned all side exhaust ports 7 to the 2nd drain passageway 13 of motor E fuel feeding, turn back to above-mentioned in the 2nd return path 14 of suction path 9 of all side draught inlets 6, the tip side binding of the appropriate location of the centre of above-mentioned the 1st drain passageway 11 and above-mentioned the 2nd drain passageway 13.In addition, above-mentioned suction path 8 and above-mentioned suction path 9 are generically and collectively referred to as suction body D (with reference to Fig. 4) sometimes.In addition, above-mentioned the 1st return path 12 and above-mentioned the 2nd return path 14 are generically and collectively referred to as return path E sometimes.
C is a pressure controlled valve, is made of valve body 20 and valve chest 30, is arranged between above-mentioned the 1st drain passageway the 11, the 1st return path the 12, the 2nd drain passageway the 13, the 2nd return path 14.Above-mentioned valve body 20 comprises the 1st valve portion 21 and thin footpath linking department 23 and the 2nd valve portion 22.The valve that will have above-mentioned the 1st valve portion 21 and the 2nd valve portion 22 is called the pressure controlled valve C of double valve type.In addition, in above-mentioned pressure controlled valve C, the slotted hole portion 31 that formation can suitably be slided with respect to above-mentioned valve body 20, in this slotted hole portion 31, the lid of fixing from the rear portion side of the 2nd valve portion 22 of above-mentioned valve body 20 33 utilizes the elastic force that compression helical spring 40 produces and always pushes to above-mentioned the 1st valve portion 21 sides.The 32nd, the stop end difference is positioned on the appropriate location of above-mentioned the 1st drain passageway 11 and is formed on the end of above-mentioned slotted hole portion 31.
For the control of above-mentioned pressure controlled valve C, have the item of the diameter of definite pressure condition, above-mentioned valve body 20, the spring constant of compression helical spring 40 etc., according to variation of the head pressure of above-mentioned the 1st drain passageway 11 etc., also need to satisfy various conditions.Particularly, need be in low rotation speed area, as shown in Figure 1, with the State Control stream of the 1st drain passageway 11 and the 2nd drain passageway 13 openings only, in the medium speed zone, as shown in Figure 2, with the 1st drain passageway 11 and the 2nd drain passageway 13 openings and 12 sealings of above-mentioned the 1st return path and the State Control stream of the 2nd return path 14 openings, in high rotary speed area, as shown in Figure 3, the State Control stream of the 1st drain passageway 11 openings and the 1st return path 12 and the 2nd return path 14 openings with 13 sealings of the 2nd drain passageway.
The action of pressure controlled valve C then, is described.At first, when outer circumferential side rotor A and interior all side rotor B are low rotation speed area, promptly when engine speed is low rotation speed area, it is the state of Fig. 1, the return path of outer circumferential side rotor A and interior all side rotor B is all stopped up by the 1st valve portion 21 of pressure controlled valve C and the 2nd valve portion 22, and the oil of discharging from the 1st drain passageway 11 and the 2nd drain passageway 13 all is discharged to the motor.Because the 1st drain passageway 11 of outer circumferential side rotor A is communicated with the 2nd drain passageway 13 of interior all side rotor B, so pressure equates.In addition, because return path is blocked, so the discharge flow rate of oil pump integral body is the flow sum of outer circumferential side rotor A and interior all side rotor B.Become the low rotation speed area of the property list (with reference to Fig. 8 B) of the property list (with reference to Fig. 8 A) of rotating speed and head pressure or rotating speed and discharge flow rate.
And then the state that rises with the rotating speed of motor is as the medium speed zone.Under this state, be the state of Fig. 2, the opening portion 141 beginning openings of the 2nd return path 14, and the opening portion 131 of the 2nd drain passageway 13 begins sealing.Describe particularly.The 2nd drain passageway 13 of the 1st drain passageway 11 of outer circumferential side rotor A and interior all side rotor B keeps being communicated with.Because the opening portion 141 beginning openings of the 2nd return path 14 of interior all side rotor B are so the rising of the pressure of all side rotor B stops at first.Simultaneously, the 1st drain passageway 11 and the 2nd drain passageway 13 are communicated with, so oil is discharged and the discharge side adverse current of inside all side rotor B and discharge the suction path 9 of all side rotor B in turning back to from the 2nd return path 14 of interior all side rotor B with this state from the outer circumferential side rotor A.Utilize this a series of active state, the pressure that the pressure that the outer circumferential side rotor A is discharged and interior all side rotor B discharge about equally.
In the medium speed zone, along with rotating speed rises, the opening portion 131 of the 2nd drain passageway 13 of interior all side rotor B is closed gradually, and the opening portion 141 of the 2nd return path 14 of interior all side rotor B is opened gradually, even if so rotating speed rises, whole flow does not increase substantially yet.The true pressure that does not display on the surface that interior all side rotor B discharge is actual because the opening portion 141 of the 2nd return path 14 of interior all side rotor B is opened gradually and slowly decline.But,,, can not descend on the pressure surface of interior all side rotor B so the pressure of outer circumferential side rotor A and interior all side rotor B is equal because the 1st drain passageway 11 is communicated with the 2nd drain passageway 13.
In addition, in the medium speed zone, owing to the opening portion 121 of the 1st return path 12 is not also opened, so the discharge flow rate of outer circumferential side rotor A is along with rotating speed increases together.In all side rotor B discharge flow rate since the opening portion 141 of the 2nd return path 14 of interior all side rotor B along with rotating speed is opened, so flow reduces.If become the above rotating speed of a certain certain value, then surpass the discharge flow rate of interior all side rotor B from the amount of the drain passageway adverse current of outer circumferential side rotor A,, the discharge flow rate of interior all side rotor B becomes negative value so offsetting.Owing to can become negative value like this,, can change in a wider range so the total flow of oil pump is the total flow of two pumps and can become flow below the pump.In this medium speed zone, in the Pressure characteristics table (with reference to Fig. 8) of rotating speed and head pressure or discharge flow rate, show, outer circumferential side rotor A monotonic increase, but interior all side rotor B sides are owing to adverse current becomes negative value, can make pressure connecting thread that outer circumferential side rotor A and interior all side rotor B add up to roughly the same with the Pressure characteristics of in the past oil pump.
With the further state that increases of the rotating speed of motor is high rotary speed area.Under this state, be the state of Fig. 3, the opening portion 121 beginning openings of the 1st return path 12, and the sealing of the opening portion 131 of the 2nd drain passageway 13 is finished.Describe particularly.Because the discharge of interior all side rotor B is fully sealed, so the drain passageway of outer circumferential side rotor A is not communicated with the drain passageway of interior all side rotor B.That is, interior all side rotor B become from outer circumferential side rotor A oil return line independently.The pressure of discharging from the outer circumferential side rotor A can't arrive interior all side rotor B, and only the 2nd return path 14 from interior all side rotor B returns, and the pressure of interior all side rotor B reduces quickly.The adverse current of inside all side rotor B also stops, and the oil of discharging from interior all side rotor B all returns via the 2nd return path 14, so the flow vanishing of flowing to motor E from interior all side rotor B.
That is, the flow vanishing of interior all side rotor B, the discharge of interior all side rotor B so friction (moment) reduces quickly, can reduce idle work all less than acting, so the efficient of pump integral body rises.In this high rotary speed area, expression in the Pressure characteristics table (with reference to Fig. 8) of rotating speed and head pressure or discharge flow rate, the outer circumferential side rotor A slowly rises, but interior all side rotor B are closed state, and the total pressure connecting thread of outer circumferential side rotor A and interior all side rotor B only is the outer circumferential side rotor A.Like this, because the reduction of the pressure of interior all side rotor B, so rub (moment) thereby the rising of reduction efficient.
Pressure for the outer circumferential side rotor A, in the medium speed zone, because the 1st drain passageway 11 is communicated with the 2nd drain passageway 13, so oil returns by the 2nd return path 14, but in high rotary speed area, owing to continue to return from the 1st return path 12, do not change so the pressure of outer circumferential side rotor is all basic in the medium speed zone and in high rotary speed area.In addition, the flow of outer circumferential side rotor A flows out to the 1st return path 12 owing to opening portion 121 openings of the 1st return path 12 and in the moment of opening, so flow just substantially no longer changes behind temporary transient decline.If describe scrupulously, then rise and atomicly rise littlely along with rotating speed.
As " pressure " of pump integral body (summation of outer circumferential side rotor A and interior all side rotor B), because opening portion 131 complete closed of the 2nd drain passageway 13 of interior all side rotor B, so only be the pressure of outer circumferential side rotor A.The pressure of outer circumferential side rotor A is owing to opening portion 121 openings of the 1st return path 12, thus not too variation, but if say scrupulously, be that the utmost point increases minutely along with the rotating speed increase.In addition, as " flow " of pump integral body, because the opening portion 131 of the 2nd drain passageway 13 of interior all side rotor B fully seal, so " flow " of outer circumferential side rotor A becomes pump integral body flow.The flow of outer circumferential side rotor A is owing to opening portion 121 openings of the 1st return path 12, thus basic not variation, but the utmost point increases minutely along with the rotating speed increase if say so scrupulously.
And then, other the mode of execution of pressure controlled valve C is described.This pressure controlled valve C is made of valve body 20 and valve chest 30, is arranged between above-mentioned the 1st drain passageway the 11, the 1st return path the 12, the 2nd drain passageway the 13, the 2nd return path 14.Above-mentioned valve body 20 comprises the 1st valve portion 21, thin footpath linking department the 22, the 3rd valve portion 24 of the 23, the 2nd valve portion and thin footpath linking department 25.Other structure is identical with Fig. 1 to Fig. 3.The valve that will have above-mentioned the 1st valve portion 21 and the 2nd valve portion 22 and the 3rd valve portion 24 is called the pressure controlled valve C of three valve types.
The effect of this pressure controlled valve C is described.At first, when outer circumferential side rotor A and interior all side rotor B are in low rotation speed area, promptly when engine speed is low rotation speed area, it is the state of Fig. 4, the return path of outer circumferential side rotor A and interior all side rotor B is all stopped up by the 1st valve portion 21 of pressure controlled valve C and the 3rd valve portion 24, and the oil of discharging from the 1st drain passageway 11 and the 2nd drain passageway 13 all is discharged to the motor.Because the 1st drain passageway 11 of outer circumferential side rotor A is communicated with the 2nd drain passageway 13 of interior all side rotor B, so pressure equates.In addition because return path is blocked, so the discharge flow rate of oil pump integral body be outer circumferential side rotor A and interior all side rotor B flow and.
And then the state that rises with the rotating speed of motor is as the medium speed zone.Under this state, be the state of Fig. 5, the opening portion 141 beginning openings of the 2nd return path 14, and the opening portion 131 of the 2nd drain passageway 13 begins sealing.Omit its explanation.With the further state that increases of the rotating speed of motor is high rotary speed area.Under this state, be the state of Fig. 6, the opening portion 121 beginning openings of the 1st return path 12, and the sealing of the opening portion 131 of the 2nd drain passageway 13 is finished.Because the discharge of interior all side rotor B is fully sealed, so the discharge of outer circumferential side rotor A is not communicated with the discharge of interior all side rotor B.That is, interior all side rotor B become from outer circumferential side rotor A oil return line independently.The pressure of discharging from the outer circumferential side rotor A can't arrive interior all side rotor B, and only the 2nd return path 14 from interior all side rotor B returns, and the pressure of interior all side rotor B reduces quickly.The adverse current of inside all side rotor B also stops, and the oil of discharging from interior all side rotor B all returns via the 2nd return path 14, so from the flow vanishing of interior all side rotor B to motor E.
That is, the flow vanishing of interior all side rotor B, the discharge of interior all side rotor B be not acting fully, so friction (moment) reduces quickly, can reduce idle work, so the efficient of pump integral body rises.In this high rotary speed area, expression in the Pressure characteristics table (with reference to Fig. 8) of rotating speed and head pressure or discharge flow rate, the outer circumferential side rotor A slowly rises, but interior all side rotor B are closed state, and the total pressure connecting thread of outer circumferential side rotor A and interior all side rotor B only is the outer circumferential side rotor A.Like this, because the reduction of the pressure of interior all side rotor B, so rub (moment) thereby the rising of reduction efficient.
Pressure for the outer circumferential side rotor A, in the medium speed zone, because the 1st drain passageway 11 is communicated with the 2nd drain passageway 13, so oil returns by the 2nd return path 14, in high rotary speed area, owing to continue to return from the 1st return path 12, do not change so the pressure of outer circumferential side rotor is all basic in the medium speed zone and in high rotary speed area.In addition, the flow of outer circumferential side rotor A flows out to the 1st return path 12 owing to opening portion 121 openings of the 1st return path 12 and in the moment of opening, so flow just substantially no longer changes behind temporary transient decline.If describe scrupulously, then rise and atomicly rise littlely along with rotating speed.
As " pressure " of pump integral body (summation of outer circumferential side rotor A and interior all side rotor B), because opening portion 131 complete closed of the 2nd drain passageway 13 of interior all side rotor B, so only be the pressure of outer circumferential side rotor A.The pressure of outer circumferential side rotor A is owing to opening portion 121 openings of the 1st return path 12, thus not too variation, but if say scrupulously, be that the utmost point increases minutely along with the rotating speed increase.In addition, as " flow " of pump integral body, because the opening portion 131 of the 2nd drain passageway 13 of interior all side rotor B fully seal, so " flow " of outer circumferential side rotor A becomes pump integral body flow.The flow of outer circumferential side rotor A is owing to opening portion 121 openings of the 1st return path 12, thus basic not variation, but the utmost point increases minutely along with the rotating speed increase if say so scrupulously.
As mentioned above, the present invention is the pressure control device of oil pump, also is the changeable flow oil pump.It is the oil pump that has two exhaust ports and use the changeable flow type of three rotors as the mechanism that these two discharge sources are provided.In addition, when the big high rotating speed of the consumption of power of pump, the exhaust port 130 of interior all side rotor B or the 2nd drain passageway 13 are blocked, so the outer circumferential side rotor A is separated with interior all side rotor B.In the flow of all side rotor B or pressure to the flow of pump integral body or pressure without any influence, so flow or the pressure of all side rotor B in regulating even if pursue efficient to improve also can not produce any influence to pump characteristics, so design freedom improves.
Claims (4)
1. the pressure control device of an oil pump is characterized in that, comprising: the oil pump that three rotors are arranged that possesses outer circumferential side rotor and interior all side rotors; From 1st drain passageway of above-mentioned outer circumferential side rotor to engine oil; Turn back to the return path of the suction side of above-mentioned outer circumferential side rotor; From 2nd drain passageway of above-mentioned interior all side rotors to engine oil; Turn back to the above-mentioned return path of the suction side of above-mentioned interior all side rotors; And the pressure controlled valve that in above-mentioned, is provided with valve body between the exhaust port of all side rotors and above-mentioned the 1st drain passageway, above-mentioned the 1st drain passageway and above-mentioned the 2nd drain passageway link, in low rotation speed area, with the State Control stream of the 1st drain passageway and the 2nd drain passageway opening only, in the medium speed zone, the State Control stream of the 2nd inlet side opening of above-mentioned return path with the 1st inlet side sealing of the 1st drain passageway and the 2nd drain passageway opening and above-mentioned return path, in high rotary speed area, the State Control stream of the 1st drain passageway opening and above-mentioned return path opening with the sealing of the 2nd drain passageway.
2. the pressure control device of an oil pump is characterized in that, comprising: the oil pump that three rotors are arranged that possesses outer circumferential side rotor and interior all side rotors; From 1st drain passageway of above-mentioned outer circumferential side rotor to engine oil; Turn back to the 1st return path of the suction side of above-mentioned outer circumferential side rotor; From 2nd drain passageway of above-mentioned interior all side rotors to engine oil; Turn back to the 2nd return path of the suction side of above-mentioned interior all side rotors; And the pressure controlled valve that in above-mentioned, is provided with valve body between the exhaust port of all side rotors and above-mentioned the 1st drain passageway, the tip side of above-mentioned the 1st drain passageway and above-mentioned the 2nd drain passageway links, in low rotation speed area, with the State Control stream of the 1st drain passageway and the 2nd drain passageway opening only, in the medium speed zone, with the 1st drain passageway and the 2nd drain passageway opening and the sealing of above-mentioned the 1st return path and the State Control stream of above-mentioned the 2nd return path opening, in high rotary speed area, the State Control stream of the 1st drain passageway opening and the 1st return path and the 2nd return path opening with the sealing of the 2nd drain passageway.
3. the pressure control device of oil pump as claimed in claim 1 or 2 is characterized in that, above-mentioned pressure controlled valve is the type with the 1st valve portion and the 2nd valve portion.
4. the pressure control device of oil pump as claimed in claim 1 or 2 is characterized in that, above-mentioned pressure controlled valve is the type with the 1st valve portion and the 2nd valve portion and the 3rd valve portion.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2007039135A JP4521005B2 (en) | 2007-02-20 | 2007-02-20 | Pressure control device in oil pump |
| JP2007-039135 | 2007-02-20 | ||
| JP2007039135 | 2007-02-20 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN101251108A true CN101251108A (en) | 2008-08-27 |
| CN101251108B CN101251108B (en) | 2011-09-14 |
Family
ID=39446211
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN2008100092597A Expired - Fee Related CN101251108B (en) | 2007-02-20 | 2008-01-31 | Oil pump pressure control device |
Country Status (6)
| Country | Link |
|---|---|
| US (1) | US20080253904A1 (en) |
| EP (1) | EP1961961B1 (en) |
| JP (1) | JP4521005B2 (en) |
| CN (1) | CN101251108B (en) |
| DE (1) | DE602007012206D1 (en) |
| ES (1) | ES2358286T3 (en) |
Cited By (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101639063B (en) * | 2009-08-21 | 2011-01-26 | 深圳益宝实业有限公司 | Gear type oil pump |
| CN102705232A (en) * | 2011-03-27 | 2012-10-03 | 株式会社山田制作所 | Pump device |
| CN102900665A (en) * | 2012-10-16 | 2013-01-30 | 李庆中 | Inside engaged gear pump or gear motor device with multilayer structure |
| CN104456036A (en) * | 2013-09-20 | 2015-03-25 | 爱信精机株式会社 | Electric oil pump |
| CN106640576A (en) * | 2016-12-09 | 2017-05-10 | 柳州职业技术学院 | Unloading type independent variable radial plunger pump |
| CN107061970A (en) * | 2016-02-11 | 2017-08-18 | Slpt国际泵业集团 | Motor vehicle lubrication pump system with two-piece type safety valve |
| CN107110152A (en) * | 2014-11-03 | 2017-08-29 | 大陆汽车有限责任公司 | Positive displacement pump |
| CN108223357A (en) * | 2017-11-24 | 2018-06-29 | 河南航天液压气动技术有限公司 | A kind of internal drainage type gear pump |
| CN109827059A (en) * | 2019-01-23 | 2019-05-31 | 浙江零跑科技有限公司 | A cycloid gear pump with bidirectional oil supply |
Families Citing this family (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP5278775B2 (en) * | 2010-12-06 | 2013-09-04 | アイシン精機株式会社 | Oil supply device |
| JP5392797B2 (en) * | 2011-12-02 | 2014-01-22 | ミュンフワ アイエヌディー． カンパニー，リミテッド | Variable oil pump |
| JP5938901B2 (en) * | 2011-12-28 | 2016-06-22 | 株式会社ジェイテクト | Motor control device and electric pump unit |
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| US4412789A (en) * | 1980-10-31 | 1983-11-01 | Jidosha Kiki Co., Ltd. | Oil pump unit |
| JPS58180790A (en) * | 1982-04-19 | 1983-10-22 | Jidosha Kiki Co Ltd | Oil pump |
| US4502845A (en) * | 1983-03-24 | 1985-03-05 | General Motors Corporation | Multistage gear pump and control valve arrangement |
| US4658583A (en) * | 1984-06-11 | 1987-04-21 | Trw Inc. | Double staged, internal rotary pump with flow control |
| DE19622688A1 (en) * | 1996-06-05 | 1997-12-11 | Bayerische Motoren Werke Ag | Internal combustion engine with separate hydraulic circuits supplied with lubricating oil |
| CA2219062C (en) * | 1996-12-04 | 2001-12-25 | Siegfried A. Eisenmann | Infinitely variable ring gear pump |
| JPH11280666A (en) * | 1998-03-27 | 1999-10-15 | Denso Corp | Fuel pump |
| JPH11280667A (en) * | 1998-03-27 | 1999-10-15 | Aisin Seiki Co Ltd | Oil pump device |
| DE69915436T2 (en) * | 1998-12-11 | 2004-07-22 | Dana Automotive Ltd., Rochester | Displacement pump systems |
| JP2002070756A (en) | 2000-08-28 | 2002-03-08 | Toyota Motor Corp | Variable displacement oil pump |
| JP4366645B2 (en) * | 2003-11-06 | 2009-11-18 | アイシン精機株式会社 | Engine oil supply device |
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- 2007-02-20 JP JP2007039135A patent/JP4521005B2/en not_active Expired - Fee Related
- 2007-12-10 EP EP07122748A patent/EP1961961B1/en not_active Not-in-force
- 2007-12-10 ES ES07122748T patent/ES2358286T3/en active Active
- 2007-12-10 DE DE602007012206T patent/DE602007012206D1/en active Active
- 2007-12-17 US US12/000,735 patent/US20080253904A1/en not_active Abandoned
-
2008
- 2008-01-31 CN CN2008100092597A patent/CN101251108B/en not_active Expired - Fee Related
Cited By (15)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101639063B (en) * | 2009-08-21 | 2011-01-26 | 深圳益宝实业有限公司 | Gear type oil pump |
| CN102705232B (en) * | 2011-03-27 | 2016-06-15 | 株式会社山田制作所 | Pump installation |
| CN102705232A (en) * | 2011-03-27 | 2012-10-03 | 株式会社山田制作所 | Pump device |
| CN102900665A (en) * | 2012-10-16 | 2013-01-30 | 李庆中 | Inside engaged gear pump or gear motor device with multilayer structure |
| CN104456036B (en) * | 2013-09-20 | 2019-03-19 | 爱信精机株式会社 | Electric oil pump |
| CN104456036A (en) * | 2013-09-20 | 2015-03-25 | 爱信精机株式会社 | Electric oil pump |
| CN107110152A (en) * | 2014-11-03 | 2017-08-29 | 大陆汽车有限责任公司 | Positive displacement pump |
| US10451060B2 (en) | 2014-11-03 | 2019-10-22 | Continental Automotive Gmbh | Positive displacement pump having multiple operating stages |
| CN107110152B (en) * | 2014-11-03 | 2019-12-06 | 大陆汽车有限责任公司 | Positive displacement pump |
| CN107061970A (en) * | 2016-02-11 | 2017-08-18 | Slpt国际泵业集团 | Motor vehicle lubrication pump system with two-piece type safety valve |
| CN107061970B (en) * | 2016-02-11 | 2019-12-10 | Slpt国际泵业集团 | Motor vehicle lubricating pump system with two-piece relief valve |
| CN106640576A (en) * | 2016-12-09 | 2017-05-10 | 柳州职业技术学院 | Unloading type independent variable radial plunger pump |
| CN108223357A (en) * | 2017-11-24 | 2018-06-29 | 河南航天液压气动技术有限公司 | A kind of internal drainage type gear pump |
| CN108223357B (en) * | 2017-11-24 | 2019-11-08 | 河南航天液压气动技术有限公司 | A kind of internal drainage type gear pump |
| CN109827059A (en) * | 2019-01-23 | 2019-05-31 | 浙江零跑科技有限公司 | A cycloid gear pump with bidirectional oil supply |
Also Published As
| Publication number | Publication date |
|---|---|
| EP1961961A2 (en) | 2008-08-27 |
| US20080253904A1 (en) | 2008-10-16 |
| JP2008202488A (en) | 2008-09-04 |
| DE602007012206D1 (en) | 2011-03-10 |
| EP1961961A3 (en) | 2009-12-16 |
| EP1961961B1 (en) | 2011-01-26 |
| JP4521005B2 (en) | 2010-08-11 |
| ES2358286T3 (en) | 2011-05-09 |
| CN101251108B (en) | 2011-09-14 |
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