CN105526032A - Variable-flow rate oil pump - Google Patents

Variable-flow rate oil pump Download PDF

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Publication number
CN105526032A
CN105526032A CN201510659721.8A CN201510659721A CN105526032A CN 105526032 A CN105526032 A CN 105526032A CN 201510659721 A CN201510659721 A CN 201510659721A CN 105526032 A CN105526032 A CN 105526032A
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CN
China
Prior art keywords
aforementioned
overflow
main
oil
valve
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Pending
Application number
CN201510659721.8A
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Chinese (zh)
Inventor
宫岛淳一
渡边贵俊
加藤悠也
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Yamada KK
Original Assignee
Yamada KK
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Filing date
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Application filed by Yamada KK filed Critical Yamada KK
Publication of CN105526032A publication Critical patent/CN105526032A/en
Pending legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01M—LUBRICATING OF MACHINES OR ENGINES IN GENERAL; LUBRICATING INTERNAL COMBUSTION ENGINES; CRANKCASE VENTILATING
    • F01M1/00—Pressure lubrication
    • F01M1/02—Pressure lubrication using lubricating pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M37/00—Apparatus or systems for feeding liquid fuel from storage containers to carburettors or fuel-injection apparatus; Arrangements for purifying liquid fuel specially adapted for, or arranged on, internal-combustion engines
    • F02M37/04—Feeding by means of driven pumps
    • F02M37/18—Feeding by means of driven pumps characterised by provision of main and auxiliary pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01M—LUBRICATING OF MACHINES OR ENGINES IN GENERAL; LUBRICATING INTERNAL COMBUSTION ENGINES; CRANKCASE VENTILATING
    • F01M1/00—Pressure lubrication
    • F01M1/16—Controlling lubricant pressure or quantity
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01M—LUBRICATING OF MACHINES OR ENGINES IN GENERAL; LUBRICATING INTERNAL COMBUSTION ENGINES; CRANKCASE VENTILATING
    • F01M1/00—Pressure lubrication
    • F01M1/12—Closed-circuit lubricating systems not provided for in groups F01M1/02 - F01M1/10
    • F01M2001/123—Closed-circuit lubricating systems not provided for in groups F01M1/02 - F01M1/10 using two or more pumps

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Details And Applications Of Rotary Liquid Pumps (AREA)
  • Lubrication Of Internal Combustion Engines (AREA)

Abstract

A variable-flow rate oil pump includes: a main oil pump; a subsidiary oil pump; a control valve provided with a spool valve body; a main discharge oil passage; a subsidiary discharge oil passage merging with the main discharge oil passage; a main relief oil passage branching from the main discharge oil passage; a subsidiary relief oil passage branching from the subsidiary discharge oil passage; and a check valve permitting a flow only in one direction from the upstream side to the downstream side of the subsidiary discharge oil passage. The control valve is positioned at respective intermediate points of the main relief oil passage and the subsidiary relief oil passage, and the control valve is positioned on the upstream side of the check valve in the subsidiary discharge oil passage, and an engine speed at which the subsidiary discharge oil passage.

Description

Changeable flow oil pump
Technical field
The invention particularly relates to the changeable flow oil pump can carrying the oil of appropriate pressure to the motor of automobile and its rotating speed accordingly.
Background technique
In the past, existed and possessed main oil pump and these two kinds of pumps of auxiliary oil pump, and the changeable flow oil pump of the FPR Fuel Pressure Regulator of the respective output quantity of adjustment.As this pump, there is patent documentation 1(Japanese Laid-Open 2013-204487).Patent documentation 1 discloses possesses adjustment from main oil pump (106) and auxiliary oil pump (107) to the oil pump unit (101) of the oil passage change-over valve (121) of the supply oil pressure of oil pressure supply destination.
Patent documentation 1: Japanese Laid-Open 2013-204487 publication.
Oil pump unit (101) disclosed in patent documentation 1 adjusts the flow direction of the output oil from main oil pump (106) and auxiliary oil pump (107) dexterously by oil passage change-over valve (121), can be supplied to motor by the oil of the appropriate pressure corresponding with the rotating speed of motor further.
If see patent documentation 1 (Fig. 7), then read and be configured with check valve (145) in the downstream of oil passage change-over valve (121).This check valve (145) is as described in paragraph [0037] and [0043], only disclose and allow oil to flow from oil passage change-over valve (121) side to merging part (142d) side, on the other hand, block oil to flow from main output channel (141) side to oil passage change-over valve (121) side.Like this, relational not open especially due to about check valve (145) and guiding valve (123), so both unexposed check valve (145) has the effect reducing fuel cost and does not also enlighten.For this reason, object of the present invention (technical problem that will solve) is to provide the changeable flow oil pump that a kind of fuel cost further reduces.
Summary of the invention
For this reason, inventor has carried out research with keen determination repeatedly in order to solve the problem, its result, be that following changeable flow oil pump solves the problems referred to above by making the 1st mode of execution of the present invention, possess: main oil pump, auxiliary oil pump, possesses the control valve of guiding valve valve body, from the main output circuit that aforementioned main oil pump extends, extend from aforementioned auxiliary oil pump and the secondary output circuit collaborated with aforementioned main output circuit, from the main overflow oil circuit of aforementioned main output circuit difference, from the secondary overflow oil circuit of aforementioned auxiliary output circuit difference, and the safety check only allowing from the side, upstream of aforementioned auxiliary output circuit to the one way flow of side, downstream, aforementioned control valve is positioned at aforementioned main overflow oil circuit and aforementioned auxiliary overflow oil circuit centre separately, aforementioned control valve is positioned at side, upstream relative to aforementioned safety check in aforementioned auxiliary output circuit, by the engine speed that aforementioned safety check blocks, aforementioned auxiliary output circuit is set to that the engine speed blocked by aforementioned guiding valve valve body than aforementioned auxiliary output circuit is low.
Be that following changeable flow oil pump solves the problems referred to above by making the 2nd mode of execution of the present invention, in the 1st mode of execution, be set to that the engine speed blocked by aforementioned safety check than aforementioned auxiliary output circuit is low by by the movement of aforementioned guiding valve valve body, oil from the engine speed of aforementioned auxiliary overflow oil circuit overflow.
Be that following changeable flow oil pump solves the problems referred to above by making the 3rd mode of execution of the present invention, possess: main oil pump, auxiliary oil pump, possesses the control valve of guiding valve valve body, from the main output circuit that aforementioned main oil pump extends, extend from aforementioned auxiliary oil pump and the secondary output circuit collaborated with aforementioned main output circuit, from the main overflow oil circuit of aforementioned main output circuit difference, from the secondary overflow oil circuit of aforementioned auxiliary output circuit difference, and the safety check only allowing from the side, upstream of aforementioned auxiliary output circuit to the one way flow of side, downstream, aforementioned control valve is positioned at aforementioned main overflow oil circuit and aforementioned auxiliary overflow oil circuit centre separately, aforementioned control valve is positioned at side, upstream relative to aforementioned safety check in aforementioned auxiliary output circuit, at the shift action by aforementioned guiding valve valve body rearward side, before aforementioned auxiliary output circuit is blocked, aforementioned auxiliary output circuit is blocked by aforementioned safety check, the overflow of the oil of aforementioned auxiliary overflow oil circuit was carried out before aforementioned safety check blocks aforementioned auxiliary output circuit.
Be that following changeable flow oil pump solves the problems referred to above by making the 4th mode of execution of the present invention, in the 1st or the 3rd mode of execution, on the valve chamber of aforementioned control valve, main overflow inflow entrance is provided with from side, front, main overflow exhaust port, secondary inflow entrance, secondary outflow opening, secondary overflow inflow entrance, and secondary overflow exhaust port, be that same position is provided with secondary inflow entrance relative to axis and aforementioned auxiliary outflow opening, be that same position is provided with secondary overflow inflow entrance relative to axis and aforementioned auxiliary overflow exhaust port, and be provided with minor diameter valve chamber in the front end of aforementioned valve chamber, aforementioned guiding valve valve body is formed by pressure valve portion from the side, front of axis towards side, rear successively, 1st large-diameter valve portion, 2nd large-diameter valve portion, and the 3rd large-diameter valve portion, aforementioned 1st large-diameter valve portion carries out the blocking-up of aforementioned main overflow inflow entrance and aforementioned main overflow exhaust port and is communicated with, aforementioned 3rd large-diameter valve portion carries out the blocking-up of aforementioned auxiliary overflow inflow entrance and aforementioned auxiliary overflow exhaust port and is communicated with, aforementionedly insert aforementioned minor diameter valve chamber by pressure valve portion, and be formed with operations flows gateway in the front end of this minor diameter valve chamber, this operations flows gateway is communicated with the operation oil circuit from aforementioned main overflow oil circuit difference, be provided with operating valve in the centre of aforementioned operation oil circuit and discharge oil circuit, aforementioned operation Vavle switching becomes aforementioned operation oil circuit to be communicated with aforementioned main overflow oil circuit, and a certain connection that aforementioned operation oil circuit is communicated with aforementioned discharge oil circuit.
Be that following changeable flow oil pump solves the problems referred to above by making the 5th mode of execution of the present invention, in the 4th mode of execution, the axial length in the 1st large-diameter valve portion of aforementioned guiding valve valve body is less than the largest interval of the axis of aforementioned main overflow exhaust port and aforementioned auxiliary outflow opening.
Be that following changeable flow oil pump solves the problems referred to above by making the 6th mode of execution of the present invention, in the 4th mode of execution, the axial length in the 1st large-diameter valve portion of aforementioned guiding valve valve body is more than or equal to the largest interval of the axis of aforementioned main overflow exhaust port and aforementioned auxiliary outflow opening.
In the present invention, along with the rotating speed of motor increases from low state, from the pressure increase of the oil that auxiliary pump exports, the guiding valve valve body of control valve rearward moves side from A-stage.And by the shift action of this guiding valve valve body rearward side, guiding valve valve body amasss with the passage sections reducing secondary output circuit gradually, and the mode of finally closing completely carries out blocking-up action.
But because the safety check being positioned at the side, downstream of control valve in secondary output circuit first carries out the blocking-up of secondary output circuit, so secondary output circuit can not be closed by guiding valve valve body completely, the flowing of the oil of secondary output circuit stops.So, auxiliary oil pump no longer carries out the work to motor transferring oil, correspondingly can reduce fuel cost.
So, solve as in the prior art find, if guiding valve valve body rearward moves side, the passage sections of secondary output circuit is long-pending to be reduced or narrows, then oil is difficult to export from auxiliary oil pump, therefore, the oil pressure of auxiliary oil pump increases, the problem that off-energy, fuel cost increase.
Accompanying drawing explanation
Figure 1A is the schematic diagram of the partly cut-away representing changeable flow of the present invention oil pump structure, Figure 1B is the enlarged view of control valve and neighbouring partly cut-away thereof, Fig. 1 C is the major component amplification view representing the state making the axial length in the 1st large-diameter valve portion of guiding valve valve body less than the largest interval of main overflow exhaust port and secondary outflow opening, and Fig. 1 D is partly cut-away's schematic diagram of operating valve;
Fig. 2 is the schematic diagram of the action of the low rotation speed area representing motor in the present invention;
Fig. 3 is the schematic diagram of the action at the initial stage in the medium speed region representing motor in the present invention;
Fig. 4 is the schematic diagram of the action in the mid-term in the medium speed region representing motor in the present invention;
Fig. 5 is the schematic diagram of the action in the later stage in the medium speed region representing motor in the present invention;
Fig. 6 is the schematic diagram of the action at the initial stage of the high speed area representing motor in the present invention;
Fig. 7 be the high speed area representing motor in the present invention mid-term first half the schematic diagram of action;
Fig. 8 is the schematic diagram of later half action in the mid-term of the high speed area representing motor in the present invention;
Fig. 9 is the schematic diagram of the action in the later stage of the high speed area representing motor in the present invention;
Figure 10 is the major component amplification view representing the state making the axial length in the 1st large-diameter valve portion of guiding valve valve body larger than the largest interval of main overflow exhaust port and secondary outflow opening,
Figure 11 is the plotted curve representing characteristic of the present invention.
Description of reference numerals:
1: main oil pump, 2: auxiliary oil pump, 31: main output circuit, 32: main overflow oil circuit, 34: operation oil circuit, 35: discharge oil circuit, 41: secondary output circuit, 42: secondary overflow oil circuit, B: control valve, 51a: secondary inflow entrance, 51b: secondary outflow opening, 52a: secondary overflow inflow entrance, 52b: secondary overflow exhaust port, 53a: main overflow inflow entrance, 53b: main overflow exhaust port, 54: minor diameter valve chamber, 54a: operations flows gateway, 6: guiding valve valve body, 61: the 1 large-diameter valve portions, 62: the 2 large-diameter valve portions, 63: the 3 large-diameter valve portions, 64: by pressure valve portion, 7: safety check, 8: operating valve.
Embodiment
Below, based on accompanying drawing, embodiments of the present invention are described.Changeable flow oil pump of the present invention was located to each portion of motor for (with reference to Fig. 1) in the oil return line 3 of oil supply.Structure of the present invention primarily of main oil pump 1, auxiliary oil pump 2, control valve B, operating valve 8, safety check 7, main output circuit 31, secondary output circuit 41, main overflow oil circuit 32, and secondary overflow oil circuit 42 is formed.And these are combined into a unit then becomes changeable flow oil pump A.
Main oil pump 1 and auxiliary oil pump 2 can use various types of pump, but the inscribed gears pump of especially preferred trochoidal curve type.Main oil pump 1 is different with the theoretical output quantity of auxiliary oil pump 2, and it is larger than auxiliary oil pump 2 that theoretical output quantity is set as main oil pump 1 mostly, but in order to increase Variable quantity, also has the situation of the theoretical output quantity increasing auxiliary oil pump 2.
Main oil pump 1 is assembled in oil return line 3, to fuel feeding objects 9 such as the motors be assembled in this oil return line 3 for oil supply (with reference to Figure 1A).The main output circuit 31 of main oil pump 1 extends from its carry-out part and is connected with fuel feeding object 9.Main output circuit 31 is parts (with reference to Figure 1A) of oil return line 3.
Auxiliary oil pump 2 is arranged side by side with aforementioned main oil pump 1 in aforementioned oil return line 3 (with reference to Figure 1A).Auxiliary oil pump 2 is adjacent or as configuring integratedly with the aforementioned main oil pump 1 of oil return line 3, or also can arrange difference oil circuit 36 from oil return line 3 in order to auxiliary oil pump 2, arranges auxiliary oil pump 2(with reference to Figure 1A in this difference oil circuit 36).
Aforementioned main output circuit 31 being provided with main overflow oil circuit 32 divaricately, when needing the overflow of main oil pump 1, carrying out overflow (discharge) via main overflow oil circuit 32.The secondary output circuit 41 collaborated with aforementioned main output circuit 31 is provided with in the output side of auxiliary oil pump 2.
On this secondary output circuit 41, be provided with relative to the output side of aforementioned auxiliary oil pump 2 the secondary overflow oil circuit 42 be connected with the suction side of auxiliary oil pump 2 divaricately from the position of side, downstream.Secondary overflow oil circuit 42 carries out overflow when needing the overflow of auxiliary oil pump 2.
At aforementioned auxiliary output circuit 41, in aforementioned main overflow oil circuit 32 and aforementioned auxiliary overflow oil circuit 42, be configured with control valve B in the suitable position of the centre of each oil circuit, these oil circuits are concentrated (with reference to Figure 1B) to a control valve B.That is, control valve B carries out the control of being communicated with of the flowing of the oil exported with auxiliary oil pump 2 from main oil pump 1 and blocking-up.
Control valve B is made up of valve chamber 5 and guiding valve valve body 6, and guiding valve valve body 6 is accommodated in (with reference to Figure 1B) in valve chamber 5.Guiding valve valve body 6 is from side, front, be configured with the 1st large-diameter valve portion 62 of large-diameter valve portion the 61,2nd and the 3rd large-diameter valve portion 63 successively, and these valve portions link via connection shaft 65 and formed.In addition, be formed by pressure valve portion 64 side on the front than aforementioned 1st large-diameter valve portion 61.Should be linked by aforementioned connection shaft 65 (with reference to Figure 1B) by pressure valve portion 64 and aforementioned 1st large-diameter valve portion 61.
At this, in this manual, if be described the front side of control valve B and rear side, then with guiding valve valve body 6 for benchmark, using aforementioned by pressure valve portion 64 or 54a side, operations flows gateway described later as front side axially, using the 3rd large-diameter valve portion 63 of guiding valve valve body 6 or spring section material 66 side described later as rear side axially.
The front side of valve chamber 5 and rear side be using the side, front with the guiding valve valve body 6 be housed in valve chamber 5 be equal direction as the front side of valve chamber 5, using its opposite side as rear side, describe front side and rear side in fig. ib.The front side of this control valve B and rear side are not only applicable to control valve B and are configured to horizontal situation as illustrated, when being applicable to be configured to vertical configuration yet.Such as, control valve B be vertical configuration, front side be positioned at above time, using upper side as front side, using side, below as rear side.
In guiding valve valve body 6, the diameter of connection shaft 65 is subject to large-diameter valve portion 62 of large-diameter valve portion of pressure valve portion the 64,1st the 61,2nd than aforementioned, and the diameter in the 3rd large-diameter valve portion 63 is little.In addition, by the diameter in pressure valve portion 64 than the 1st large-diameter valve portion 62 of large-diameter valve portion the 61,2nd, and the diameter in the 3rd large-diameter valve portion 63 is little.1st large-diameter valve portion of large-diameter valve portion of large-diameter valve portion the 61,2nd the 62,3rd 63 is same diameter (with reference to Figure 1B).
Be subject to pressure valve portion 64,1st large-diameter valve portion 61,2nd large-diameter valve portion 62 and the 3rd large-diameter valve portion 63 respective between there is gap part, the 1st gap part 61s is called by between pressure valve portion 64 and the 1st large-diameter valve portion 61, be called the 2nd gap part 62s between 1st large-diameter valve portion 61 and the 2nd large-diameter valve portion 62, between the 2nd large-diameter valve portion 62 and the 3rd large-diameter valve portion 63, be called that the 3rd gap part 63s(is with reference to Figure 1B).
Guiding valve valve body 6 can in valve chamber 5 vertically before and after reciprocate, in the side, rear end of guiding valve valve body 6, be namely equipped with the spring section materials 66 such as compression helical spring between the 3rd large-diameter valve portion 63 and the rear end side of valve chamber 5, when guiding valve valve body 6 is flat to the side, front of valve chamber 5 by elastic force-applying.And guiding valve valve body 6 is positioned at the state of side, front stopping to greatest extent as A-stage in valve chamber 5.
The aforementioned minor diameter valve chamber 54 inserted by pressure valve portion 64 is formed in the end of the side, front of valve chamber 5.In minor diameter valve chamber 54, as described later, oil is admitted to via the operation oil circuit 34 from main overflow oil circuit 32 difference, and being rearward pushed side by pressure valve portion 64 of side, front, guiding valve valve body 6 rearward side moves.
In valve chamber 5, be provided with secondary inflow entrance 51a as the attachment portion involved by auxiliary oil pump 2, secondary outflow opening 51b, secondary overflow inflow entrance 52a, and secondary overflow exhaust port 52b.In addition, in aforementioned valve chamber 5, main overflow inflow entrance 53a and main overflow exhaust port 53b is provided with as the attachment portion involved by main oil pump 1.
And, from the side, front of valve chamber 5, be formed with main overflow inflow entrance 53a successively, main overflow exhaust port 53b, secondary outflow opening 51b, and secondary overflow exhaust port 52b, secondary inflow entrance 51a and secondary outflow opening 51b are same position in the axial direction, secondary overflow inflow entrance 52a and secondary overflow exhaust port 52b is same position (with reference to Figure 1B) in the axial direction.
By the 1st large-diameter valve portion 61 and the 2nd large-diameter valve portion 62 of guiding valve valve body 6, by between main overflow inflow entrance 53a and main overflow exhaust port 53b, and be communicated with between secondary inflow entrance 51a with secondary outflow opening 51b and block (with reference to Fig. 2 to Fig. 9).In addition, by the 3rd large-diameter valve portion 63 and the 2nd large-diameter valve portion 62, will be communicated with between secondary overflow inflow entrance 52a with secondary overflow exhaust port 52b and block (with reference to Fig. 2 to Fig. 9).
Aforementioned auxiliary output circuit 41 is divided into be located at middle control valve B for benchmark the 1st secondary output circuit 41a is connected with secondary inflow entrance 51a side, and the be connected with secondary outflow opening 51b side the 2nd secondary output circuit 41b(reference Figure 1A).Aforementioned 1st secondary output circuit 41a auxiliary connection oil pump 2 and control valve B, aforementioned 2nd secondary output circuit 41b connection control valve B and main output circuit 31(are with reference to Figure 1A).
In addition, the 1st secondary overflow oil circuit 42a that secondary overflow oil circuit 42 is connected with secondary overflow inflow entrance 52a side for benchmark is divided into be located at middle control valve B, and the 2nd secondary overflow oil circuit 42 be connected with secondary overflow exhaust port 52b side.Aforementioned 1st secondary overflow oil circuit 42a, from aforementioned 1st secondary output circuit 41a difference, is connected with secondary overflow inflow entrance 52a.In addition, aforementioned 2nd secondary overflow oil circuit 42b is connected to the suction side of aforementioned auxiliary oil pump 2 or the difference oil circuit 36 of aforementioned auxiliary oil pump 2 from secondary overflow exhaust port 52b.
The 1st main overflow oil circuit 32a that aforementioned main overflow oil circuit 32 is connected with main overflow inflow entrance 53a side for benchmark is divided into control valve B, and the be connected with main overflow exhaust port 53b side the 2nd main overflow oil circuit 32b(is with reference to Figure 1A).2nd main overflow oil circuit 32b connects at the interflow, position of the top trip side of ratio main oil pump 1 of the suction side of main oil pump 1 or oil return line 3.
The aforementioned minor diameter valve chamber 54 of aforementioned valve chamber 5 is formed with operations flows gateway 54a.And, be formed between this operations flows gateway 54a and aforementioned 1st main overflow oil circuit 32a and operate oil circuit 34.Operating valve 8 is configured with in the intermediate portion of this operation oil circuit 34.
Operating valve 8 possesses position control valve portion 81.In addition, in operating valve 8, be equipped with discharge oil circuit 35.And, by the operation of operating valve 8, can become to be only operations flows gateway 54a and to be communicated with the 1st main overflow oil circuit 32a by handover operation, with a certain connection (reference Figure 1B, Fig. 1 D) that operations flows gateway 54a is communicated with aforementioned discharge oil circuit 35.Operating valve 8 uses solenoid valve, but also can use hydraulic type valve.
Safety check 7 is provided with in the 2nd secondary output circuit 41b of aforementioned auxiliary output circuit 41.Safety check 7 uses (with reference to Figure 1B) as check valve.Safety check 7 only allows oil to flow from the side, upstream of the 2nd secondary output circuit 41b to side, downstream, and blocks the reverse flow of oil.
That is, only oil can be carried to the direction of collaborating with main output circuit 31 from the secondary outflow opening 51b of control valve B, then cannot on the contrary.Safety check 7 is formed (with reference to Figure 1B) by spheroid 71 with to elastic force-applying portion materials 72 such as the compression helical springs that this spheroid 71 exerts a force.
In addition, safety check 7 is acted as spheroid 71 by resilient biasing member 72 and blocks flowing from from the side, upstream of the 2nd secondary output circuit 41b to side, downstream, at the flow velocity hour of the oil flowed out from the secondary outflow opening 51b of control valve B, power due to resilient biasing member 72 is greater than the power of the oil pressure difference that flow velocity produces, so can stop the flowing of oil.
In addition, in control valve B, the length La of the axis in the 1st large-diameter valve portion 61 of guiding valve valve body 6 is set to less than the largest interval Lb of the main overflow exhaust port 53b of valve chamber 5 and the axis of secondary outflow opening 51b.I.e. La<Lb.
The main overflow exhaust port 53b of valve chamber 5 and secondary outflow opening 51b can not close by the 1st large-diameter valve portion 61 simultaneously completely, and becomes the state that one party opens.That is, close in the 1st large-diameter valve portion 61 before secondary outflow opening 51b terminates, main overflow exhaust port 53b opens and can start the overflow of main oil pump 1.So, if stop due to the output of oil to the secondary output circuit 41 of auxiliary oil pump 2, then can start the overflow of main oil pump 1 swimmingly, prevent the variation sharply of pressure, so vibration and noise can be reduced.
In addition, in control valve B, the length La of the axis in the 1st large-diameter valve portion 61 of guiding valve valve body 6 is set to that the largest interval Lb(being more than or equal to the main overflow exhaust port 53b of valve chamber 5 and the axis of secondary outflow opening 51b is with reference to Figure 10).I.e. La >=Lb.
In above-mentioned size relationship, the oil exported from main oil pump 1 can make to move from the engine speed of main overflow oil circuit 32 overflow to slightly high rotary speed area side.In other words, extend to more side, high speed area by the engine speed in the medium speed region (later stage) by low fuel pressure, fuel cost can be made to reduce.
Then, with action of the present invention for the main low rotation speed area to motor, medium speed region and high speed area are described.In accompanying drawing, the arrow recorded along each oil circuit represents oily flowing.In addition, in the rotation status of motor, also comprise idling (also crying idle rotation).
In the low rotation speed area of motor, as shown in Figure 2, the state of the guiding valve valve body 6 of control valve B is A-stage.And main overflow exhaust port 53b closes by the 1st large-diameter valve portion 61, secondary inflow entrance 51a and secondary outflow opening 51b opens by the 2nd gap part 62s.In addition, secondary overflow inflow entrance 52a and secondary overflow exhaust port 52b closes by the 3rd large-diameter valve portion 63.
In addition, operating valve 8 makes main overflow oil circuit 32 be connected state with operation oil circuit 34 in advance, and oil flows into minor diameter valve chamber 54 from operations flows gateway 54a, but the elastic force of the force rate spring section material 66 of its oil pressure generation is little, and guiding valve valve body 6 is A-stage.
So, main oil pump 1 will export oil to main output circuit 31, to fuel feeding objects 9 such as motors for oil supply.Main oil pump 1 and auxiliary oil pump 2 all do not carry out overflow.Auxiliary oil pump 2 exports oil to secondary output circuit 41, intactly supplies oil supply to fuel feeding object 9 from the place, interflow with main output circuit 31.
That is, main oil pump 1 and auxiliary oil pump 2 are all that full output quantity intactly supplies to fuel feeding object 9.At this, relative to the safety check 7 be equipped in the 2nd secondary output circuit 41b, the elastic force of the force rate resilient biasing member 72 that the flow velocity from the oil of auxiliary oil pump 2 produces is large, and therefore, oil flows in the 2nd secondary output circuit 41b.
Then, as shown in Figures 3 to 5, be divided into just to the initial stage after medium speed zone-transfer, engine speed is the mid-term of meta, and is described close to the later stage of high speed area in the medium speed region of motor.After just transferring to medium speed region from rotary speed area, flow into the pressure increase of the oil of minor diameter valve chamber 54, the power that oil pressure produces is greater than the elastic force of spring section material 66, and guiding valve valve body 6 rearward side moves slightly.And the 3rd large-diameter valve portion 63 moves, secondary overflow inflow entrance 52a and secondary overflow exhaust port 52b is opened.That is, the 3rd gap part 63s is positioned at secondary overflow inflow entrance 52a and secondary overflow exhaust port 52b.
But the A-stage in this medium speed region, due to guiding valve valve body 6 only movement on a small quantity, so secondary overflow inflow entrance 52a and secondary overflow exhaust port 52b shifts from blocking state slightly to open mode, starts a small amount of overflow (with reference to Fig. 3).That is, auxiliary oil pump 2 supplies oil supply via secondary output circuit 41 to main output circuit 31, and also marginally carries out overflow.
In the mid-term in medium speed region, the guiding valve valve body 6 of control valve B further rearward side move.So, the area of opening of secondary inflow entrance 51a and secondary outflow opening 51b is closed to small degree by the 1st large-diameter valve portion 61.In this stage, the oil exported from auxiliary oil pump 2 flow from secondary inflow entrance 51a to secondary outflow opening 51b, but the elastic force of the resilient biasing member 72 of the force rate safety check 7 of the flow velocity of oil now generation is little.Its result, safety check 7 stops the flowing of oil.
Therefore, oil is stopped from auxiliary oil pump 2 to the supply of fuel feeding object 9, and auxiliary oil pump 2 only becomes overflow action.In addition, relative to fuel feeding object 9, oil only supplies from main oil pump 1.Now, the overflow action of main oil pump 1 is not started.
In the later stage in medium speed region, as shown in Figure 5, the guiding valve valve body 6 of control valve B further rearward side move.And the 1st large-diameter valve portion 61 becomes the side rearward, position than main overflow inflow entrance 53a and main overflow exhaust port 53b, and the 1st gap part 61s makes it be communicated with between main overflow inflow entrance 53a with main overflow exhaust port 53b.
And the 1st main overflow oil circuit 32a is communicated with the 2nd main overflow oil circuit 32b, start the overflow of the main oil pump 1 that main overflow oil circuit 32 produces.That is, main oil pump 1 for oil supply, also carries out overflow action from main output circuit 31 to fuel feeding object 9 simultaneously.
Then, the high speed area of motor as shown in Figures 6 to 9, is divided into the initial stage, mid-term first half, mid-term is later half, and the later stage is described.At the initial stage of high speed area, as shown in Figure 6, operating valve 8 is operated, operation oil circuit 34 is communicated with discharge oil circuit 35.So, the oil in the minor diameter valve chamber 54 of valve chamber 5 is discharged from discharge oil circuit 35, by spring section material 66, guiding valve valve body 6 is forwards moved side.That is, guiding valve valve body 6 becomes the A-stage identical with during low rotation speed area.
And secondary inflow entrance 51a and secondary outflow opening 51b opens by the 1st large-diameter valve portion 61, via the 2nd gap part 62s, the 1st secondary output circuit 41a is communicated with the 2nd secondary output circuit 41b.So, oil flows to secondary output circuit 41 again, from main output circuit 31 to fuel feeding object 9 for oil supply.That is, by main oil pump 1 and auxiliary oil pump 2, oil supplies to fuel feeding object 9.
In the first half in mid-term of high speed area, as shown in Figure 7, by the rising of the output pressure of main oil pump 1, the main overflow inflow entrance 53a of oil from main output circuit 31 to control valve B sends into.And the upper outside power adding oil pressure and produce in the 1st large-diameter valve portion 61, guiding valve valve body 6 rearward side moves.In addition, in the first half in mid-term of this high speed area, become not to the structure by the additional oil pressure in pressure valve portion 64 of guiding valve valve body 6, but because the oil pressure of the oil flowed in the 1st main overflow oil circuit 32a increases, so guiding valve valve body 6 moves by means of only the power of the oil pressure be only added on the compression face in the 1st large-diameter valve portion 61.
Moved by this, secondary overflow inflow entrance 52a and secondary overflow exhaust port 52b opens by the 3rd large-diameter valve portion 63, and the 1st secondary output circuit 41a is communicated with the 2nd secondary output circuit 41b, starts the overflow of auxiliary oil pump 2.In this stage, main oil pump 1 not overflow, to fuel feeding object 9 for oil supply, auxiliary oil pump 2 carries out overflow to fuel feeding object 9 for oil supply.
Later half in the mid-term of high speed area, as shown in Figure 8, by the further rising of the output pressure of main oil pump 1, guiding valve valve body 6 rearward side moves.And secondary output circuit 41 is blocked, and auxiliary oil pump 2 only carries out overflow.Main oil pump 1 supplies oil supply to fuel feeding object 9, but does not carry out overflow.
In the later stage of high speed area, as shown in Figure 9, by the further rising of the output pressure of main oil pump 1, guiding valve valve body 6 rearward side moves.And secondary output circuit 41 is blocked, and auxiliary oil pump 2 only carries out overflow.Main oil pump 1 supplies oil supply to fuel feeding object 9, and carries out overflow.The low rotation speed area of above motor, the pressure of oil in medium speed region and high speed area and the relation table of rotating speed are shown in the plotted curve of expression characteristic of the present invention of Figure 11.
In the 2nd mode of execution, before being blocked by safety check at secondary output circuit, make oil from the structure of secondary overflow oil circuit overflow, further can reduce the oil pressure of auxiliary oil pump, therefore, it is possible to seek the further reduction of fuel cost.In the 3rd mode of execution, the every speed region of the fuel feeding object such as motor relative to automobile can be provided, the changeable flow oil pump of the oil with more appropriate oil pressure can be supplied.Especially relative to medium speed region and the high speed area of motor, very carefully can set the oil pressure of the oil of supply, further improve the efficiency of lubrication.
Safety check can prevent oil from flowing from main output circuit to secondary output circuit.That is, the adverse current of the oil in secondary output circuit can be prevented, correctly carry out the work that auxiliary oil pump carries out.In addition, aforementioned safety check be oil pressure difference before and after the safety check that produces at the flow velocity because of aforementioned auxiliary output circuit small time block the structure of oil circuit.
So, aforementioned guiding valve valve body moves to the side, rear of valve chamber, even if secondary overflow outflow opening is not closed completely, but the gap of slightly oil flow, the flow velocity of oil is also weak, and safety check can stop the flowing of the oil of secondary output circuit.And, the useless oil pressure of the oil supplied relative to fuel feeding object via main output circuit from auxiliary oil pump can be suppressed to rise.In addition there is the effect equal with mode of execution 1.
In the 4th mode of execution, the structure that can be used in mobile guiding valve valve body is simple.And, owing to being provided with operating valve in the centre of operation oil circuit and discharging oil circuit, aforementioned operation Vavle switching operates into aforementioned operation oil circuit and is communicated with aforementioned main overflow oil circuit, and a certain connection that aforementioned operation oil circuit is communicated with aforementioned discharge oil circuit, so the shift action of guiding valve valve body is smooth and easy and reliably.
In the 5th mode of execution, because the axial length in the 1st large-diameter valve portion of guiding valve valve body is less than the largest interval of the axis of aforementioned main overflow exhaust port and aforementioned auxiliary outflow opening, so the state being about to the fuel feeding stopping secondary output circuit to be formed and the overflow action that just started secondary overflow oil circuit overlap in time, the moment oil pressure or the impact of sudden turn of events generation of flow velocity that can reduce that action switches.
In the 6th mode of execution, axial length due to the 1st large-diameter valve portion of guiding valve valve body is more than or equal to the largest interval of the axis of aforementioned main overflow exhaust port and aforementioned auxiliary outflow opening, so after can stopping from the fuel feeding of secondary output circuit, start the overflow action of main oil pump, carry out reliable fuel feeding and overflow action.

Claims (6)

1. a changeable flow oil pump, it is characterized in that, possess: main oil pump, auxiliary oil pump, possesses the control valve of guiding valve valve body, from the main output circuit that aforementioned main oil pump extends, extend from aforementioned auxiliary oil pump and the secondary output circuit collaborated with aforementioned main output circuit, from the main overflow oil circuit of aforementioned main output circuit difference, from the secondary overflow oil circuit of aforementioned auxiliary output circuit difference, and the safety check only allowing from the side, upstream of aforementioned auxiliary output circuit to the one way flow of side, downstream, aforementioned control valve is positioned at aforementioned main overflow oil circuit and aforementioned auxiliary overflow oil circuit centre separately, aforementioned control valve is positioned at side, upstream relative to aforementioned safety check in aforementioned auxiliary output circuit, by the engine speed that aforementioned safety check blocks, aforementioned auxiliary output circuit is set to that the engine speed blocked by aforementioned guiding valve valve body than aforementioned auxiliary output circuit is low.
2. changeable flow oil pump as claimed in claim 1, is characterized in that, is set to that the engine speed blocked by aforementioned safety check than aforementioned auxiliary output circuit is low by by the movement of aforementioned guiding valve valve body, oil from the engine speed of aforementioned auxiliary overflow oil circuit overflow.
3. a changeable flow oil pump, it is characterized in that, possess: main oil pump, auxiliary oil pump, possesses the control valve of guiding valve valve body, from the main output circuit that aforementioned main oil pump extends, extend from aforementioned auxiliary oil pump and the secondary output circuit collaborated with aforementioned main output circuit, from the main overflow oil circuit of aforementioned main output circuit difference, from the secondary overflow oil circuit of aforementioned auxiliary output circuit difference, and the safety check only allowing from the side, upstream of aforementioned auxiliary output circuit to the one way flow of side, downstream, aforementioned control valve is positioned at aforementioned main overflow oil circuit and aforementioned auxiliary overflow oil circuit centre separately, aforementioned control valve is positioned at side, upstream relative to aforementioned safety check in aforementioned auxiliary output circuit, at the shift action by aforementioned guiding valve valve body rearward side, before aforementioned auxiliary output circuit is blocked, aforementioned auxiliary output circuit is blocked by aforementioned safety check, the overflow of the oil of aforementioned auxiliary overflow oil circuit was carried out before aforementioned safety check blocks aforementioned auxiliary output circuit.
4. the changeable flow oil pump as described in claim 1 or 3, it is characterized in that, on the valve chamber of aforementioned control valve, main overflow inflow entrance is provided with from side, front, main overflow exhaust port, secondary inflow entrance, secondary outflow opening, secondary overflow inflow entrance, and secondary overflow exhaust port, be that same position is provided with secondary inflow entrance relative to axis and aforementioned auxiliary outflow opening, be that same position is provided with secondary overflow inflow entrance relative to axis and aforementioned auxiliary overflow exhaust port, and be provided with minor diameter valve chamber in the front end of aforementioned valve chamber, aforementioned guiding valve valve body is formed by pressure valve portion from the side, front of axis towards side, rear successively, 1st large-diameter valve portion, 2nd large-diameter valve portion, and the 3rd large-diameter valve portion, aforementioned 1st large-diameter valve portion carries out the blocking-up of aforementioned main overflow inflow entrance and aforementioned main overflow exhaust port and is communicated with, aforementioned 3rd large-diameter valve portion carries out the blocking-up of aforementioned auxiliary overflow inflow entrance and aforementioned auxiliary overflow exhaust port and is communicated with, aforementionedly insert aforementioned minor diameter valve chamber by pressure valve portion, and be formed with operations flows gateway in the front end of this minor diameter valve chamber, this operations flows gateway is communicated with the operation oil circuit from aforementioned main overflow oil circuit difference, be provided with operating valve in the centre of aforementioned operation oil circuit and discharge oil circuit, aforementioned operation Vavle switching becomes aforementioned operation oil circuit to be communicated with aforementioned main overflow oil circuit, and a certain connection that aforementioned operation oil circuit is communicated with aforementioned discharge oil circuit.
5. changeable flow oil pump as claimed in claim 4, is characterized in that, the axial length in the 1st large-diameter valve portion of aforementioned guiding valve valve body is less than the largest interval of the axis of aforementioned main overflow exhaust port and aforementioned auxiliary outflow opening.
6. changeable flow oil pump as claimed in claim 4, it is characterized in that, the axial length in the 1st large-diameter valve portion of aforementioned guiding valve valve body is more than or equal to the largest interval of the axis of aforementioned main overflow exhaust port and aforementioned auxiliary outflow opening.
CN201510659721.8A 2014-10-16 2015-10-14 Variable-flow rate oil pump Pending CN105526032A (en)

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JP2016070219A (en) * 2014-09-30 2016-05-09 株式会社山田製作所 Oil pump structure
WO2016055082A1 (en) * 2014-10-09 2016-04-14 Volvo Truck Corporation An oil pump assembly for a vehicle lubrication system
WO2017034565A1 (en) * 2015-08-27 2017-03-02 Borgwarner Inc. Solenoid-actuated pressure-relief valve
JP6518282B2 (en) * 2017-03-28 2019-05-22 株式会社Ｓｕｂａｒｕ Oil supply device

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JP5923361B2 (en) * 2012-03-28 2016-05-24 株式会社山田製作所 Engine with variable flow oil pump
JP2013204487A (en) 2012-03-28 2013-10-07 Honda Motor Co Ltd Engine with variable flow rate oil pump

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