CN100419267C - No-load operation system of tadem pump - Google Patents
No-load operation system of tadem pump Download PDFInfo
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- CN100419267C CN100419267C CNB2005800319603A CN200580031960A CN100419267C CN 100419267 C CN100419267 C CN 100419267C CN B2005800319603 A CNB2005800319603 A CN B2005800319603A CN 200580031960 A CN200580031960 A CN 200580031960A CN 100419267 C CN100419267 C CN 100419267C
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- sliding spool
- pressure
- draining
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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
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B23/00—Pumping installations or systems
- F04B23/04—Combinations of two or more pumps
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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
- F04C2270/00—Control; Monitoring or safety arrangements
- F04C2270/56—Number of pump/machine units in operation
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Multiple-Way Valves (AREA)
- Fluid-Pressure Circuits (AREA)
- Details And Applications Of Rotary Liquid Pumps (AREA)
Abstract
When the pressure in the main oil supply channel 9 is lower than the no-load operation start pressure, the pressurized oil within the secondary oil supply channel 10 passes through the internal flow channel 21 of the spool 20 and flows into the main oil supply channel 9. At this time oil output from both the main and secondary oil pumps 7, 8 is merged and supplied to the oil supply destination OB. When the pressure within the main oil supply channel 9 rises and reaches the no-load operation start pressure, the spool 20 moves in opposite direction to the direction of the force of the spring 30, the pressurized oil within the secondary oil supply channel 10 is drained, the poppet 40 contacts the spool 20 and blocks the internal flow channel 21 of the spool 20. At this time, the secondary oil pump 8 enters the no-load operation state, and oil output from the main oil pump 7 only is transmitted to the oil supply destination OB.
Description
Technical field
The present invention relates to have two fluid pumps driving simultaneously by a driving source, make the pressure oil interflow that two fluid pumps discharge and supply to the pumps in series that fluid is supplied with the structure of object.In more detail, relate in the delivery volume of fluid and increasing and fluid when supplying with pressure in the road and reaching the no-load operation initiation pressure, make a fluid pump carry out no-load operation so that seek to save the no-load operation device of pumps in series of the power of driving source.
Background technique
Pumps in series has two fluid pumps that driven simultaneously by a driving source, can discharge the pressure oil of identical or different pressure from two fluid pumps exhaust port separately.Though this pumps in series is connected in two different drivers of two exhaust ports and can makes these drivers carry out work respectively respectively, but supply to a fluid by the pressure oil interflow that two pumps are discharged and supply with object, can also obtain the flow of two fluid pumps.As the use example of the latter's pumps in series, have for example be located in the motor car engine, supply to the oil pump that is located at the oil duct in the engine cylinder-body being used for oil (machine oil) lubricated and cooling in each one of motor.It becomes the structure that is driven the live axle of pumps in series by the gear on the bent axle that is installed on motor.Low in engine speed, from the discharge of two oil pumps oil flow hour, the discharge oil of two oil pumps collaborates in the fuel feeding road, when the oily flow of the discharge of engine speed height, two oil pumps is big, make an oily draining of discharge of two oil pumps and become the no-load operation state, only the discharge oil of another oil pump supplies in the fuel feeding road.In this structure, even because the rotating speed of motor also can be guaranteed sufficient lubricant oil delivery volume when low, so even also each parts of lubricating engine etc. fully during low vehicle speeds.This pumps in series for example, discloses in Japanese kokai publication hei 10-131751 communique, TOHKEMY 2001-132624 communique etc.
One of no-load operation device of known pumps in series example in the past shown in Fig. 7.In Fig. 7, main oil pump P1 and auxiliary oil pump P2 are driven simultaneously by a driving source (motor M).The main fuel feeding road L1 that extends from the exhaust port of main oil pump P1 is connected in fuel feeding object (for example being located at the oil duct in the engine cylinder-body) OB via not shown in-line filter.In addition, the secondary fuel feeding road L2 that extends from the exhaust port of auxiliary oil pump P2 is connected with the intermediate portion of main fuel feeding road L1.On secondary fuel feeding road L2, clamp prevent from main fuel feeding road L1 to auxiliary oil pump P2 side inflow working oil one-way valve CV, be provided with feather valve AV between one-way valve CV in secondary fuel feeding road L2 and the auxiliary oil pump P2.
At this, when the pressure in low, the main fuel feeding of the rotating speed at the motor road L1 hangs down, feather valve AV becomes closed condition, because the discharge oil of auxiliary oil pump P2 flows into main fuel feeding road L1 by one-way valve CV, so the discharge oil of major-minor two oil pump P1, P2 is sent to fuel feeding object OB with the state that collaborates from main fuel feeding road L1.On the other hand, when the rotating speed of motor improves and the discharge oil flow of two oil pumps increases, if the pressure in the main fuel feeding road L1 reaches the no-load operation initiation pressure when above, pressure oil in the then main fuel feeding road L1 is opened feather valve AV via the sliding spool of hydraulic control oil circuit LP pushing feather valve AV, working oil in the secondary fuel feeding road L2 is opened to the draining side, and auxiliary oil pump P2 becomes idling.At this moment, one-way valve CV closes secondary fuel feeding road L2 because the pressure in the secondary fuel feeding road L2 reduces, so only the discharge oil of main oil pump P1 supplies to fuel feeding object OB.In addition, in main fuel feeding road L1, be provided with relief valve (pressure regulator valve) LV, the pressure in the fuel feeding road L1 of winner just can not reached more than the overflow set pressure.
Summary of the invention
In above-mentioned pumps in series in the past, because relief valve (pressure regulator valve) LV that is located at one-way valve CV and the feather valve AV among the secondary fuel feeding road L2 and is located among the main fuel feeding road L1 constitutes separately independently valve respectively, so the degrees of freedom of the layout the during design of loop is restricted, exists the such problem of miniaturization that is difficult to seek whole device.
The present invention makes in view of such problem, and purpose is to provide a kind of both to have been had and equal in the past function, can seek the no-load operation device of pumps in series of formation of the miniaturization of whole device again.
No-load operation device according to pumps in series of the present invention comprises: pumps in series, and it has main fluid pump (for example, the main oil pump in the mode of execution 7) and the secondary fluid pump (for example, the auxiliary oil pump in the mode of execution 8) that is driven simultaneously by driving source; Main fluid is supplied with road (for example, the main fuel feeding road 9 in the mode of execution), and its exhaust port from above-mentioned main fluid pump is supplied with object (for example, the fuel feeding object OB in the mode of execution) to fluid and extended; Secondary fluid is supplied with road (for example, the secondary fuel feeding road 10 in the mode of execution), and its exhaust port from above-mentioned secondary fluid pump extends and is connected with the intermediate portion on above-mentioned main fluid supply road; Valve opening, it constitutes the part that above-mentioned secondary fluid is supplied with the road; Sliding spool, it is configured to insert in the above-mentioned valve opening removable the cooperation freely, has the internal flow path that extends vertically; Force application component (for example, the spring 30 in the mode of execution) is supplied with the joint side that the road is connected to above-mentioned sliding spool towards this valve opening and above-mentioned main fluid and is applied power in above-mentioned valve opening; The seat valve core, the above-mentioned sliding spool of ratio in above-mentioned valve opening is more supplied with the joint side that the road is connected by this valve opening with above-mentioned main fluid, be configured to and in above-mentioned valve opening, move freely, this seat valve core can move between closed position and open position, this closed position be the end of this seat valve core and above-mentioned sliding spool above-mentioned internal flow path the end butt and with its position of blocking, this open position is that this seat valve core leaves from the end of above-mentioned internal flow path and the position that opens it.The draining stream is connected setting with above-mentioned valve opening, above-mentioned sliding spool is subjected to that above-mentioned main fluid supplies with that pressure in the road overcomes the power that applies of above-mentioned force application component and removable, pressure in above-mentioned main fluid is supplied with the road is during less than the no-load operation initiation pressure, above-mentioned sliding spool is by the power that applies of above-mentioned force application component and to supplying with the joint side shifting on road with above-mentioned main fluid, being communicated with and making above-mentioned secondary fluid supply with the road via above-mentioned internal flow path of blocking-up and above-mentioned draining stream is communicated with above-mentioned main fluid supply road, pressure in above-mentioned main fluid is supplied with the road rises and when surpassing above-mentioned no-load operation initiation pressure, above-mentioned sliding spool overcomes the applying power of above-mentioned force application component and moves, thereby making above-mentioned secondary fluid supply with the road is connected with above-mentioned draining stream, owing to above-mentioned secondary fluid is supplied with above-mentioned secondary fluid that the pressure oil in the road produced by draining and is supplied with the poor of pressure in road and the above-mentioned main fluid supply road, the end butt of the above-mentioned internal flow path of above-mentioned seat valve core and above-mentioned sliding spool and be moved to above-mentioned with its position of closing.
In addition, in the no-load operation device of above-mentioned pumps in series, preferably, be provided with draining dual-purpose stream from this both sides' opening of outer circumferential face of road and above-mentioned seat valve core to above-mentioned main fluid that supply with in the inside of above-mentioned seat valve core, when above-mentioned main fluid is supplied with pressure in the road and is reached the overflow set pressure of high pressure more above above-mentioned no-load operation initiation pressure, above-mentioned sliding spool is subjected to the pushing force of above-mentioned overflow set pressure and moves to the position that above-mentioned draining dual-purpose stream is connected with above-mentioned draining stream, makes above-mentioned main fluid supply with pressure oil in the road from above-mentioned draining stream draining.
In the no-load operation device of pumps in series of the present invention, when the pressure in main fluid is supplied with the road was lower than the no-load operation initiation pressure, the pressure oil that secondary fluid is supplied with in the road was supplied with in the road by the internal flow path inflow main fluid of sliding spool.At this moment, the discharge oil from two fluid pumps of major-minor is sent to fluid supply object with the state that collaborates.Pressure in main fluid is supplied with the road rises and when reaching above-mentioned no-load operation initiation pressure, sliding spool makes secondary fluid supply with pressure oil draining in the road to moving in the opposite direction with the application of force side of force application component, the seat valve core contacts with sliding spool and closes the internal flow path of sliding spool.At this moment, the secondary fluid pump becomes the no-load operation state, and only the discharge oil with the main fluid pump is sent to fluid supply object.So in the no-load operation device of pumps in series of the present invention, owing to both maintain secondary fluid supply with pressure in the road rise make when reaching above-mentioned no-load operation initiation pressure the secondary fluid pump become the no-load operation state save the power of driving source (and then the pressure in main fluid is supplied with the road makes the pressure oil overflow in the main fluid supply road when reaching overflow set pressure) such with equal in the past function, in a valve opening, has sliding spool again as essential member, force application component and seat valve core, so the degrees of freedom of the layout the during design of loop improves, and can seek the miniaturization of whole device.
Description of drawings
Fig. 1 is the sectional view of structure of no-load operation device of the pumps in series of expression one embodiment of the present invention.
Fig. 2 is the exploded sectional view of above-mentioned no-load operation device.
Fig. 3 is the exploded perspective view of the interior formation product that had of valve body.
Fig. 4 is the sliding spool of the discharge oil of expression major-minor two oil pumps when being sent to the fuel feeding object with the state at interflow and the figure of one of the operating position of seat valve core example.
Fig. 5 is that the vice oil pump becomes the no-load operation state and the figure of one of sliding spool when only the discharge oil of main oil pump is sent to the fuel feeding object and operating position of seat valve core example.
Fig. 6 is that expression discharges that head pressure in the stream reaches overflow set pressure and the part of the head pressure of the main oil pump sliding spool during by overflow and the figure of one of the operating position of seat valve core example.
Fig. 7 is the hydraulic circuit diagram of structure example of representing the no-load operation device of pumps in series in the past.
Embodiment
Below, with reference to accompanying drawing preferred forms of the present invention is described.Fig. 1 illustrates the no-load operation device of the pumps in series of one embodiment of the present invention.This no-load operation device is located in the motor car engine, be used for the oil (machine oil) lubricated and cooling that is used for of each one of motor (for example is sent to the fuel feeding object, the not shown oil duct that is located in the engine cylinder-body) OB, this no-load operation device is assembled in the pump housing of being made up of the part of the crankcase of motor 1.In the pump housing 1, form pump chamber 2, wherein be provided with pumps in series 3.Pumps in series 3 constitutes by actuation gear 4 with at two driven gears (the 1st driven gear 5 and the 2nd driven gear 6) of its both sides and actuation gear 4 external engagements, actuation gear 4 is by live axle 4a rotation supporting freely, and the 1st and the 2nd driven gear 5,6 is respectively by driven shaft 5a, 6a rotation supporting freely.The live axle 4a of actuation gear 4 is driven by the bent axle (not shown) of motor, rotates to the direction of arrow shown in Fig. 1 (being rotated counterclockwise).The 1st driven gear 5 and the 2nd driven gear 6 rotate to the direction of arrow shown in Fig. 1 (turning clockwise) respectively along with the rotation of actuation gear 4.
As mentioned above, pumps in series 3 has main oil pump 7 and the auxiliary oil pump 8 that is driven simultaneously by a driving source (motor).And main fuel feeding road 9 is connected in the exhaust port 7b of main oil pump 7 and extends, and secondary fuel feeding road 10 (10a, 10b, 10c) is connected in the exhaust port 8b of auxiliary oil pump 8 and extends.Main fuel feeding road 9 is connected in not shown fuel feeding object OB, and secondary fuel feeding road 10 (10a, 10b, 10c) is connected in the intermediate portion on main fuel feeding road 9 as shown in Figure 1.In addition, the 1st oily inlet passage 11 that is connected in the suction port 7a of main oil pump 7 is connected in food tray T, and the 2nd oily inlet passage 12 that is connected in the suction port 8a of auxiliary oil pump 8 is connected in the intermediate portion of the 1st oily inlet passage 11.
In secondary fuel feeding road 10, valve opening 13 extends so that constitute the part on this pair fuel feeding road 10, and insertion is provided with integral body and is sliding spool 20 cylindraceous (also with reference to Fig. 2 and Fig. 3) this valve opening 13 in.As shown in Figure 1, this sliding spool 20 comprises the intermediate portion 22 that has vertically the internal flow path 21 that extends, be located at the left side (left side among Fig. 1) of this intermediate portion 22 and to the spring accommodating part 23 that the round-ended cylinder shape is arranged of left opening, this sliding spool 20 moves freely on the bearing of trend on secondary fuel feeding road 10 valve opening 13 in and disposes.In spring accommodating part 23, accommodate the right side part that is disposed at the spring 30 in the spring holding space 14 that is formed in the pump housing 1, sliding spool 20 by this spring 30 all the time towards right-hand (the main fuel feeding road 9 sides) application of force.The sliding spool retainer 51 and the discoid application of force that accommodate hollow cylindrical in spring holding space 14 are adjusted tool 52, by the end plate 53 sealing spring holding spaces 14 that are installed in the plate mounting groove 15 that is located on the pump housing 1.In addition, adjust the power that applies that tool 52 can suitably be adjusted spring 30 by changing the different application of force of used thickness.
With the step-like sliding spool bearing surface 13a that is formed with, be formed with seat valve core receiving bore 13d in the right part of valve opening 13 on its right side.As described later, the opening 13e of seat valve core receiving bore 13d and its right part constitutes the part on secondary fuel feeding road 10.
Sliding spool 20 is subjected to the power that applies of spring 30 and moves to the right in valve opening 13, can move to sliding spool 20 main fuel feeding road 9 sides (paper right side among Fig. 1) end 28 (with reference to Fig. 2) be formed on sliding spool bearing surface 13a (with reference to Fig. 2) butt in the valve opening 13 till, below, the position of sliding spool 20 of this moment is called " initial position " of sliding spool 20.Moreover sliding spool 20 is positioned at the leftmost side in valve opening 13 position is the end 23a of spring accommodating part 23 during from end 51a (seeing figures.1.and.2) butt of right-hand and sliding spool retainer 51, it is called " moving position, a maximum left side ".
Dispose the seat valve core 40 that bottom tube-like is arranged in the present spool receiving bore 13d, moving axially freely along sliding spool 20 in this seat valve core 40 present spool receiving bore 13d to main fuel feeding road 9 side openings.Seat valve core 40 has portion 41 and seat portion 42, and the external diameter of this one 41 is bigger, and this one 42 is positioned at the left side (sliding spool 20 sides) of this one 41 and external diameter less than the external diameter of tube portion 41, is formed with radially a plurality of intercommunicating pore 43b of perforation in the present portion 42.
On the substantial middle part of the intermediate portion 22 of sliding spool 20, be provided with the sliding spool neck 25 of external diameter less than its axial both sides.Be formed with the 26a of left and right sides sliding spool shoulder portion, 26b about this sliding spool neck 25, the 26a of this left and right sides sliding spool shoulder portion, 26b cooperate in the insertion valve opening 13 (13b, 13c).Be provided with a plurality of intercommunicating pores 27 along outer circumferential face on the left sliding spool shoulder 26a of portion, these intercommunicating pores 27 are connected with internal flow path 21.In addition, be formed with the draining that radially connects with opening 29 on right-hand right sliding spool shoulder 26b of portion of sliding spool neck 25, this draining also is connected with internal flow path 21 with opening 29.
Secondary fuel feeding road 10 is divided into by the part that constitutes in the valve opening 13 (becoming stream 10b), part (becoming stream 10a) and the part from valve opening 13 to main fuel feeding road 9 (becoming stream 10c) from the exhaust port 8b of auxiliary oil pump 8 to valve opening 13 is illustrated, even sliding spool 20 moves to " moving position, a maximum left side " from " initial position ", intercommunicating pore 27 also is connected with stream 10a all the time.
Space between the seat hole 13b of the outer circumferential face of sliding spool neck 25 and valve opening 13 forms working oil path 16, and this working oil path 16 is connected with the draining stream 17 that leads to food tray T via the 2nd oily inlet passage 12.Though be positioned under the state of initial position at sliding spool 20 or from initial position under the state that left moves on a small quantity, cooperate with seat hole 13b and stop being communicated with of stream 10a and working oil path 16 by sliding spool neck 26, but further under the state that left moves, stream 10a is communicated with working oil path 16 at sliding spool 20.
As shown in Figure 2, the assembling of this no-load operation device is performed such: after adjusting seat valve core 40, sliding spool 20, spring 30, sliding spool retainer 51 and the application of force in the valve opening 13 (with sliding spool hole 13d) that tool 52 is inserted into the pump housing 1 successively, be inserted in the plate mounting groove 15 of the pump housing 1 at the following end plate 53 of state that makes spring 30 contractions by adjust tool 52 with the finger press application of force.
In the no-load operation device of the pumps in series 3 with this structure, when actuation gear 4 was driven in rotation, the 1st driven gear 5 and the 2nd driven gear 6 that mesh with actuation gear 4 also were rotated, and main oil pump 7 carries out pump action respectively with auxiliary oil pump 8.Specifically, main oil pump 7 sucks oil in the food tray T from suction port 7a, discharges from exhaust port 7b.Auxiliary oil pump 8 sucks oil in the food tray T from suction port 8a in addition, discharges from exhaust port 8b.
Becoming these fuel feeding object OB that discharge the supply destination of oil is the interior oil ducts of engine cylinder-body, is according to the increase of supplying with oil mass and the structure that supply pressure improves.Therefore, when the rotating speed of motor hanged down, because the discharge of two oil pumps of major-minor 7,8 oil flow is also little, the pressure in the fuel feeding road 9,10 was also low.Here, from the head pressure of auxiliary oil pump 8 act on internal flow path 21 to left to sliding spool 20 application of forces.Therefore, sliding spool 20 overcomes the power that applies of spring 30 and moves to the left of initial position, but because head pressure is low, so amount of movement is little, as shown in Figure 4, being communicated with because of sliding spool shoulder portion 26 of secondary fuel feeding road 10a and working oil path 16 was prevented from cooperating of the 13b of seat portion.At this moment, the oil that is discharged in the stream 10a just all flows in the internal flow path 21 of sliding spool 20.
Flow into the discharge oil in the internal flow path 21 like this, seat valve core 40 is pushed open 9 rear flank, main fuel feeding road (the seat portion 42 of seat valve core 40 is left from the seat portion 24 of sliding spool 20) flow into (with reference to flowing of the oil shown in the arrow of Fig. 4) in the main fuel feeding road 9 from auxiliary oil pump 8.Therefore, discharge oil oily from the discharge of main oil pump 7 and from auxiliary oil pump 8 is sent to fuel feeding object OB with the state that collaborates from main fuel feeding road 9.Though the discharge oil flow of two oil pumps of major-minor this moment 7,8 is very little respectively, owing to be to be sent to fuel feeding object OB behind the both sides interflow, so as totally guaranteeing enough lubricant oil delivery volumes.
Then, when the rotating speed of motor improved, then the discharge of two oil pumps of major-minor 7,8 oil flow also increased, so the pressure in the fuel feeding road 9,10 also raises.Sliding spool 20 further moves to left thus.Then, when the pressure in the fuel feeding road 9,10 reaches the no-load operation initiation pressure, as shown in Figure 5, sliding spool shoulder portion 26 right parts all are positioned at stream 10a, stream 10a is communicated with working oil path 16, and the part of the discharge oil of auxiliary oil pump 8 is got back to food tray T from stream 10a via working oil path 16 and draining stream 17.That is, the power that applies that sliding spool 20 overcomes spring 30 moves and secondary fuel feeding road 10 is connected with draining stream 17 to left, the pressure oil draining in the secondary thus fuel feeding road 10a.
Pressure in the internal flow path 21 of secondary thus fuel feeding road 10a and sliding spool 20 reduces.As a result, owing to produce pressure reduction between pressure in main fuel feeding road 9 and the pressure in the secondary fuel feeding road 10a,, be pressed against the seat portion 24 of sliding spool 20 so seat valve core 40 moves to left.Become being communicated with of main fuel feeding road 9 and secondary fuel feeding road 10a thus by the state of seat valve core 40 blocking-up, and because seat valve core 40 is applied power to sliding spool 20 to left by the pushing of the pressure in the main fuel feeding road 9, so sliding spool 20 moves to left all the more, the flow of getting back to the pressure oil of food tray T from stream 10a via working oil path 16 and draining stream 17 increases, and all gets back to food tray T from the discharge oil of auxiliary oil pump 8.
Auxiliary oil pump 8 becomes the no-load operation state thus, has saved the power that drives the driving source (motor) of pumps in series 3.Moreover, though only be sent to fuel feeding object OB from main fuel feeding road 9 this moment from the discharge oil of main oil pump 7, because the discharge of main oil pump 7 oil flow has reached enough big, so can guarantee the necessary lubricant oil delivery volume of fuel feeding object OB.
The rotating speed of this rear engine further improves, and increases more from the oily flow of the discharge of main oil pump 7, and the head pressures of thereupon discharging in the stream 9 also improve, but this head pressure acts on seat valve core 40.Therefore, seat valve core 40 is subjected to main fuel feeding road 9 (with stream 10c) Yi Bian interior pressure moves to left pushing sliding spool 20 on one side.Then, when the head pressure from main oil pump 7 reaches overflow set pressure, be located at draining on the right sliding spool shoulder 26b of portion of sliding spool 20 with opening 29 to draining stream 17 inner openings, the part of the pressure oil in the main fuel feeding road 9 flows in the draining stream 17 with opening 29 by being located at draining dual-purpose stream 43 in the seat valve core 40 and the draining that is located on the sliding spool 20 from stream 10c, gets back to food tray T (with reference to Fig. 6).That is, when the pressure in the main fuel feeding road 9 reaches overflow set pressure when above, then draining dual-purpose stream 43 is connected with draining stream 17 with opening 29 via draining, makes the interior pressure oil draining in main fuel feeding road 9.
The effect of relief valve (pressure regulator valve) is played in the draining action (overflow action) of the pressure oil in the main fuel feeding road 9 of being undertaken by this sliding spool 20 and seat valve core 40; by this overflow action; can prevent that the pressure in the main fuel feeding road 9 from surpassing predetermined maximum pressure (overflow set pressure), guarantees the safety in loop.
Moreover as mentioned above, when the pressure oil in main fuel feeding road 9 was begun the rotating speed decline of motor by the state of overflow, 40 pairs of sliding spools 20 of seat valve core weakened to the power that applies of the left application of force, and sliding spool 20 moves to right-hand under the active force of spring 30.Then, when the draining on being formed at sliding spool 20 was closed by the seat hole 13c of valve opening 13 with opening 29, the pressure oil in the main fuel feeding road 9 can not flow in the draining stream 17 above-mentioned overflow release (with reference to Fig. 5).And when engine speed further descended, sliding spool 20 further moved to right-hand under the active force of spring 30.Then, when the seat hole 13b of the sliding spool shoulder portion 26 of sliding spool 20 and the pump housing 1 was relative, the pressure oil of (in the stream 10a) can not flow into draining stream 17 in the secondary fuel feeding road 10, and the no-load operation state of auxiliary oil pump 8 finishes (with reference to Fig. 4).
Moreover, as mentioned above, " the no-load operation initiation pressure " of auxiliary oil pump 8 beginning no-load operations, " overflow set pressure " that begin overflow with pressure oil in the main fuel feeding road 9 can be set arbitrarily by the spring performance of spring 30 or initial displacement (displacement of the spring 30 when sliding spool 20 is in initial position).Therefore when above-mentioned no-load operation initiation pressure of change or overflow set pressure, as long as spring 30 is replaced with the different spring of spring performance or application of force adjustment tool 52 is replaced with the different parts of thickness.
So in the no-load operation device of the pumps in series shown in the present embodiment, because having when the pressure that both maintains in the secondary fuel feeding road 10 reaches the no-load operation initiation pressure makes auxiliary oil pump 8 become the power that the no-load operation state is saved driving source, and then the pressure in main fuel feeding road 9 make when reaching overflow set pressure pressure oil overflow in the main fuel feeding road 9 such with equal in the past function, in a valve opening 13, has sliding spool 20 again as essential member, spring 30 and seat valve core 40, so the degrees of freedom of the layout the during design of loop is improved, and can seek the miniaturization of whole device.
Moreover, in the above-described embodiment, because the inside of present spool 40 is provided with the draining dual-purpose stream 43 with this both sides' opening of outer circumferential face of seat valve core 40 to main fuel feeding road 9, and draining opening 29 is set in valve opening 13, when the pressure in the main fuel feeding road 9 reaches overflow set pressure, draining dual-purpose stream 43 be connected with opening 29 with draining and pressure oil in the main fuel feeding road 9 by draining, thereby sliding spool 20, seat valve core 40 and spring 30 also play the effect of relief valve, but also can above-mentioned draining dual-purpose stream 43 and draining with opening 29, and in main fuel feeding road 9, relief valve is set in addition.In such structure, though relief valve need be set in addition, but since will be in structure in the past sliding spool, seat valve core and the spring of member of effect of performance one-way valve and feather valve be received in the valve opening, so compared with the pastly can obtain the structure simple such effect that becomes fully.
So far preferred forms of the present invention is illustrated, but scope of the present invention is not limited to the form shown in the above-mentioned mode of execution.For example, though in the above-described embodiment, the present invention illustrates as the example of being located in the engine for automobile, the oil pressure of the lubricated of each one of motor and cooling usefulness is delivered to fuel feeding object OB such as oil duct, but this is an example, and the object that oil is supplied with limits especially.Thereby, also can be taken as fluid driver to the supply object of the oil in this device, use as the device of control according to the movement speed of the driver of load etc.In addition, though in the above-described embodiment, it is oil that pumps in series is discharged the fluid of supplying with, and this fluid is not limited to oil, also can be water or air etc.Two fluid pumps that driven simultaneously by a driving source in addition, constitute by gear pump, so long as also can be the pumps (for example vane pump or reciprocating pump etc.) of other forms though constitute two fluid pumps of pumps in series.
Claims (8)
1. the no-load operation device of a pumps in series is characterized in that having:
Pumps in series, it has main fluid pump and the secondary fluid pump that is driven simultaneously by driving source;
Main fluid is supplied with the road, and its exhaust port from above-mentioned main fluid pump is supplied with object to fluid and extended;
Secondary fluid is supplied with the road, and its exhaust port from above-mentioned secondary fluid pump extends and is connected with the intermediate portion on above-mentioned main fluid supply road;
Valve opening, it constitutes the part that above-mentioned secondary fluid is supplied with the road;
Sliding spool, it is configured to insert in the above-mentioned valve opening removable the cooperation freely, has the internal flow path that extends vertically;
Force application component is supplied with the joint side that the road is connected to above-mentioned sliding spool towards this valve opening and above-mentioned main fluid and is applied power in above-mentioned valve opening;
The seat valve core, the above-mentioned sliding spool of ratio in above-mentioned valve opening is more supplied with the joint side that the road is connected by this valve opening with above-mentioned main fluid, be configured to and in above-mentioned valve opening, move freely, this seat valve core can move between closed position and open position, this closed position be the end of this seat valve core and above-mentioned sliding spool above-mentioned internal flow path the end butt and with its position of blocking, this open position is that this seat valve core leaves from the end of above-mentioned internal flow path and the position that opens it
The draining stream is connected setting with above-mentioned valve opening, and above-mentioned sliding spool is subjected to that above-mentioned main fluid supplies with that pressure in the road overcomes the power that applies of above-mentioned force application component and removable,
Pressure in above-mentioned main fluid is supplied with the road is during less than the no-load operation initiation pressure, above-mentioned sliding spool is by the power that applies of above-mentioned force application component and to supplying with the joint side shifting on road with above-mentioned main fluid, being communicated with and making above-mentioned secondary fluid supply with the road via above-mentioned internal flow path of blocking-up and above-mentioned draining stream is communicated with above-mentioned main fluid supply road
Pressure in above-mentioned main fluid is supplied with the road rises and when surpassing above-mentioned no-load operation initiation pressure, above-mentioned sliding spool overcomes the applying power of above-mentioned force application component and moves, thereby making above-mentioned secondary fluid supply with the road is connected with above-mentioned draining stream, supply with above-mentioned secondary fluid that the pressure oil in the road produced by draining and supply with the poor of pressure in road and the above-mentioned main fluid supply road owing to above-mentioned secondary fluid, above-mentioned seat valve core is moved to above-mentioned closed position.
2. the no-load operation device of pumps in series according to claim 1 is characterized in that,
Above-mentioned pumps in series is made of gear pump, and this gear pump constitutes by actuation gear that driving source drove with the 1st driven gear and the 2nd driven gear of the external engagement of this actuation gear.
3. the no-load operation device of pumps in series according to claim 1 is characterized in that,
Above-mentioned sliding spool constitutes by the intermediate portion with above-mentioned internal flow path with in the one-sided force application component accommodating part that is subjected to the power that applies of above-mentioned force application component of above-mentioned intermediate portion,
On the axial central part at the peripheral part place of above-mentioned intermediate portion, be provided with the sliding spool neck of minor diameter, and about this sliding spool neck, being provided with sliding spool shoulder portion, above-mentioned left and right sides sliding spool shoulder portion cooperates with above-mentioned valve opening and removable the insertion freely of above-mentioned sliding spool is arranged in the above-mentioned valve opening.
4. the no-load operation device of pumps in series according to claim 3 is characterized in that,
Be provided with the intercommunicating pore that connects outer circumferential face and is communicated with above-mentioned internal flow path in above-mentioned left sliding spool shoulder portion, above-mentioned intercommunicating pore is connected with the discharge oral-lateral of above-mentioned secondary fluid pump in the above-mentioned secondary fluid supply road in the moving range of above-mentioned sliding spool all the time.
5. according to the no-load operation device of claim 3 or 4 described pumpss in series, it is characterized in that,
Pressure in above-mentioned main fluid is supplied with the road surpasses above-mentioned no-load operation initiation pressure and above-mentioned sliding spool overcomes the power that applies of above-mentioned force application component and when mobile, make above-mentioned secondary fluid supply with the road via above-mentioned sliding spool neck and be connected with above-mentioned draining stream.
6. the no-load operation device of pumps in series according to claim 1 is characterized in that,
Be provided with draining dual-purpose stream from this both sides' opening of outer circumferential face of road and above-mentioned seat valve core to above-mentioned main fluid that supply with in the inside of above-mentioned seat valve core, when the pressure in the above-mentioned main fluid supply road reaches than its higher overflow set pressure above above-mentioned no-load operation initiation pressure, above-mentioned sliding spool is subjected to the pushing force of above-mentioned overflow set pressure and moves to the position that above-mentioned draining dual-purpose stream is connected with above-mentioned draining stream, makes above-mentioned main fluid supply with pressure oil in the road from above-mentioned draining stream draining.
7. the no-load operation device of pumps in series according to claim 6 is characterized in that,
Above-mentioned sliding spool constitutes by the intermediate portion with above-mentioned internal flow path with in the one-sided force application component accommodating part that is subjected to the power that applies of above-mentioned force application component of above-mentioned intermediate portion,
On the axial central part at the peripheral part place of above-mentioned intermediate portion, be provided with the sliding spool neck of minor diameter, and about this sliding spool neck, be provided with sliding spool shoulder portion, cooperate with above-mentioned valve opening by above-mentioned left and right sides sliding spool shoulder portion, above-mentioned sliding spool is moved to insert freely and is arranged in the above-mentioned valve opening.
8. the no-load operation device of pumps in series according to claim 7 is characterized in that,
Be provided with the draining opening in above-mentioned right sliding spool shoulder portion, this draining penetrates into outer circumferential face with opening, from being communicated to the part that above-mentioned main fluid is supplied with trackside by the part of the above-mentioned seat valve core obturation in the above-mentioned internal flow path,
When above-mentioned main fluid is supplied with pressure in the road and is reached above-mentioned overflow set pressure, above-mentioned sliding spool is subjected to the pushing force of above-mentioned overflow set pressure and moves to the position that above-mentioned draining is communicated with above-mentioned draining stream with opening, thereby above-mentioned draining dual-purpose stream is connected with above-mentioned draining stream.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP274855/2004 | 2004-09-22 | ||
| JP2004274855 | 2004-09-22 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN101027485A CN101027485A (en) | 2007-08-29 |
| CN100419267C true CN100419267C (en) | 2008-09-17 |
Family
ID=36089971
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CNB2005800319603A Expired - Fee Related CN100419267C (en) | 2004-09-22 | 2005-08-03 | No-load operation system of tadem pump |
Country Status (5)
| Country | Link |
|---|---|
| US (1) | US20080107545A1 (en) |
| EP (1) | EP1806504A1 (en) |
| JP (1) | JPWO2006033207A1 (en) |
| CN (1) | CN100419267C (en) |
| WO (1) | WO2006033207A1 (en) |
Families Citing this family (10)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP5007085B2 (en) * | 2006-08-15 | 2012-08-22 | 株式会社Ｔｂｋ | Tandem pump valve structure |
| DE102006056844A1 (en) * | 2006-12-01 | 2008-06-05 | Robert Bosch Gmbh | Internal gear pump |
| JP5232842B2 (en) * | 2010-09-16 | 2013-07-10 | 株式会社山田製作所 | Variable flow oil pump |
| JP5232843B2 (en) * | 2010-09-16 | 2013-07-10 | 株式会社山田製作所 | Variable flow oil pump |
| JP5923361B2 (en) | 2012-03-28 | 2016-05-24 | 株式会社山田製作所 | Engine with variable flow oil pump |
| CN103277505B (en) * | 2013-05-30 | 2015-10-28 | 长城汽车股份有限公司 | Automobile, automatic transmission and hybrid-power hydraulic control system |
| CN105370567B (en) * | 2015-12-14 | 2017-08-29 | 贵州红林机械有限公司 | Automatic partial pressure type duplex gear pump |
| US9657561B1 (en) | 2016-01-06 | 2017-05-23 | Isodrill, Inc. | Downhole power conversion and management using a dynamically variable displacement pump |
| US9464482B1 (en) | 2016-01-06 | 2016-10-11 | Isodrill, Llc | Rotary steerable drilling tool |
| CN106050763B (en) * | 2016-08-15 | 2018-01-05 | 阜新北鑫星液压有限公司 | One kind turns control constant current hydraulic oil pump |
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Also Published As
| Publication number | Publication date |
|---|---|
| US20080107545A1 (en) | 2008-05-08 |
| CN101027485A (en) | 2007-08-29 |
| EP1806504A1 (en) | 2007-07-11 |
| JPWO2006033207A1 (en) | 2008-05-15 |
| WO2006033207A1 (en) | 2006-03-30 |
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