CN203655624U - Variable displacement vane pump - Google Patents
Variable displacement vane pump Download PDFInfo
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- CN203655624U CN203655624U CN201320796601.9U CN201320796601U CN203655624U CN 203655624 U CN203655624 U CN 203655624U CN 201320796601 U CN201320796601 U CN 201320796601U CN 203655624 U CN203655624 U CN 203655624U
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Abstract
The utility model discloses a variable displacement vane pump. The variable displacement vane pump comprises an eccentric ring (2), a rotor (3) and an adjusting mechanism for adjusting the eccentric distance of the eccentric ring (2) and the rotor (3). The variable displacement vane pump is characterized by further comprising a pilot valve (4) for driving the adjusting mechanism to change the eccentric distance of the eccentric ring (2) and the rotor (3); and the pilot valve (4) is communicated with the adjusting mechanism by an oil pipe (5). With the adoption of the structure disclosed by the utility model, the pilot valve is controlled to avoid feeding back oil pressure information from a pump cavity so as to avoid hysteresis and errors of displacement adjustment; and meanwhile, the interferences to a control system, caused by a pressure drop phenomenon under a high speed, are also avoided, so that a high-speed safety pressure value is improved without manual work and the optimal energy utilization rate is realized.
Description
Technical field
The utility model relates to the oil pump in motor car engine field, relates to particularly a kind of variable displacement vane pump.
Background technique
Along with the development of modernized society, automobile has more and more been come into people's life as a kind of important traffic tool.And as the motor of automobile core component, the quality of its lubrication system directly has influence on performance and the life-span of motor.The lubrication system of orthodox car motor is to drive oil hydraulic-pump rotor to rotate by engine shaft in simple terms, be located at epitrochanterian some blade rotation thereby drive, by the eccentric setting of oil pump inner chamber and rotating shaft, make the chamber of the different volume size that described in blade rotation process, some blades surround be compressed and expand, finally realize negative pressure oil suction and high pressure oil transportation.As can be seen here, in such oil pump, after the eccentric distance between its lumen centers and shaft axis is fixing, the output quantity size of its high-voltage oil liquid providing is determined by engine speed completely, is referred to as constant flow pump.Therefore, not hard to imagine, when automobile is during in high speed operation, the conveying of its fluid is excessive waste often.This does not obviously meet in development of automobile process, the policy of high-efficient energy-saving environment friendly.
And there is in the prior art the adjustable variable-displacement pump of so a kind of fluid output quantity, the patent of invention that for example patent No. is 200580043674.9, its design principle is on the basis of traditional constant flow pump, to set up a control ring in simple terms, described control ring is located in the cavity of oil pump, and be placed on described blade and rotor makes blade and rotor rotate outward in the chamber of described control ring, and one end of this control ring is fixed on the inwall of oil pump, its the other end is provided with the controlling mechanism for regulating control ring to swing, make the eccentric distance between the lumen centers of control ring and the axis of rotating shaft adjustable by controlling mechanism thus, thereby change the compressed degree of fluid, change the discharge capacity of fluid, finally meet the fluid voltage stabilizing output of automobile under different speed per hours.Therefore, the workflow of this variable-displacement pump is that first inductor detects cavity inner fluid force value, feeds back to system, judges force value size by system, then by regulating and controlling mechanism, control ring is swung, and adjusts to best displacement position.This technological scheme also becomes the base of design of existing variable-displacement pump in the industry.And for this prior art, the but following several point defects of objective reality:
1 inductor detects that the pressure information of fluid feeds back to system, order about control ring by system regulating and controlling mechanism again and swing, but in the middle of a process, because described control ring is often larger, therefore due to the inertia of himself, the adjusting of this fluid discharge capacity certainly exists hysteresis quality.
Described in 2, control ring certainly exists certain friction between itself and pump housing inwall in swing process, no matter be the two directly frictional force of contact, or the frictional force producing by Sealing, all contrary with moving direction all the time, therefore this frictional force will cause the required power in control ring swing front and back not identical, will make thus the control of controlling mechanism have error, thereby cause the error of system control.
3 in the time that motor car engine runs up, and the compressed degree of described fluid also can be aggravated, thus at the negative pressure region of cavity volume because cavitation phenomenons will produce bubble.Therefore the equilibrant in described cavity volume will be broken, and negative pressure region is because bubble will be lost part hydraulic coupling, thereby makes pressurizing area produce the moment of torsion of an emission reduction to control ring, makes motor in high speed processes, have a pressure drop.A difficult problem for this high speed pressure drops namely always existing in the industry, thus in the industry in order to meet the safety pressure requirement of fast state, often need the standard of artificial its high speed pressure of raising for overcoming above-mentioned pressure drop phenomena.Have no alternative but thus cause the energy dissipation of certain fast state.
Model utility content
The technical problems to be solved in the utility model is that a kind of accurately timely and high variable displacement vane pump of fast state capacity usage ratio of controlling is provided.
Technical solution of the present utility model is, provide a kind of variable displacement vane pump with following structure: it comprises the eccentric hoop of being located in described pump chamber, with the rotor of the inner chamber eccentric setting of described eccentric hoop with for regulating the controlling mechanism of described eccentric hoop and rotor eccentricity distance, between one side of the outer circle wall of described eccentric hoop and the inwall of pump chamber, pass through straight pin chain connection, its opposite side is provided with extension arm, it is characterized in that, described variable displacement vane pump also comprises the pilot valve for driving controlling mechanism that the eccentric distance of eccentric hoop and rotor is changed, between described pilot valve and controlling mechanism, be connected by oil pipe.
Particularly, described controlling mechanism comprises emission reduction chamber, increase displacement chamber and Returnning spring, the contrary side with respect to rotor eccentricity position of described extension arm is located in described emission reduction chamber, by the first Sealing, be located at the seal ring on straight pin, eccentric hoop sidewall and pump chamber inwall surround, described increasing displacement chamber is located at a side contrary with emission reduction chamber on described extension arm, and by the second Sealing, be located at the seal ring on straight pin, eccentric hoop sidewall and pump chamber inwall surround, described Returnning spring is located in described increasing displacement chamber and its one end is resisted against on described extension arm, its the other end is resisted against on pump chamber inwall.
As a kind of improvement of the present utility model, described pilot valve comprises valve body, be located at the spool that can slide axially in described valve body and the preloading spring for pretension spool, the week of described valve body is upwards provided with the first hydraulic fluid port, the second hydraulic fluid port and unloading port, described spool is provided with for being communicated with the first hydraulic fluid port with the first hydraulic pressure cavity of the second hydraulic fluid port with for being communicated with the second hydraulic pressure cavity of the second hydraulic fluid port and unloading port, in described valve body, be also provided with three hydraulic fluid port corresponding with spool bottom, the top of described spool is also provided with containing groove, one end of described preloading spring is located in described containing groove, its the other end and valve body lean.By the design of pilot valve, realize the cavity in the corresponding corresponding controlling mechanism of different hydraulic fluid ports, thereby the pressure by pilot valve regulates regulating and controlling mechanism, and therefore the feedback of oil liquid pressure information directly completes in pilot valve, has avoided the interference of the disturbing factor in pump chamber to oil liquid pressure information.
Preferred as one, the spool bottom that described the 3rd hydraulic fluid port is corresponding be circumferentially equipped with the second chamfering, described valve body is provided with first chamfering corresponding with described the second chamfering, and described the first chamfer angle is greater than the angle of described the second chamfering.In the time that the first chamfer angle is greater than the second chamfer angle, in the work of set solid amount, be that the low side of spool runs to when approaching in valve body chamber lower end surface most, can effectively avoid both ends of the surface directly to fit, therefore also just discharged in the time that spool is switched to other working state from the work of set solid amount the transient state pressure fluctuation causing due to face area flip-flop.
Further, the 4th hydraulic fluid port corresponding to described the first hydraulic fluid port, the 3rd hydraulic fluid port and emission reduction chamber is all connected with main hydraulic fluid port by oil pipe, and described the second hydraulic fluid port is connected with increasing displacement chamber.
As another kind of improvement of the present utility model, between described preloading spring and valve body, be provided with elastic force controlling device, between one end of described elastic force controlling device and valve body, be threaded, its other end is provided with boss, and the end face of described boss and one end of preloading spring lean.Can control described boss rising or decline by screwing elastic force controlling device, thereby can change the pretightening force of preloading spring, can regulate the voltage stabilizing value at steady oil transportation place.
As last a kind of improvement of the present utility model, described variable displacement vane pump also comprises solenoid valve, described spool is provided with the 3rd hydraulic pressure cavity that makes spool overcome preloading spring, and described solenoid valve is connected with main hydraulic fluid port and the 3rd hydraulic pressure cavity respectively, and described solenoid valve is electrically connected with control system.By setting up solenoid valve and the 3rd hydraulic pressure cavity, control spool that can be artificial overcomes the oil liquid pressure of preloading spring, thereby variable-displacement pump can be improved as to twin-stage, if certainly set up multiple solenoid valves, it can be multistage again.
Adopt above structure, the utility model compared with prior art has the following advantages: first, emission reduction chamber in controlling mechanism is communicated with main hydraulic fluid port, increasing displacement chamber is connected with main oil pipe by the first hydraulic fluid port, the first hydraulic pressure cavity and second hydraulic fluid port of pilot valve, therefore can increase by pilot valve control the fluid connected sum unloading of displacement chamber, thus the output of the discharge capacity of control oil pump.So as long as the oil liquid pressure in feedback pilot valve, this has also been avoided feeding back from pump chamber hysteresis quality and the error that oil pressure information causes.Secondly, after the feedback information of oil pressure directly obtains from pilot valve, also avoided the interference to control system of pressure drop phenomena under high speed, therefore improved high-speed secure force value without artificial going, thereby realized best capacity usage ratio.
Accompanying drawing explanation
Fig. 1 is structural representation of the present utility model.
Fig. 2 is that the utility model is removed the internal structure schematic diagram after pump cover and pilot valve.
Fig. 3 is the cross section structure schematic diagram of " A " direction in Fig. 1.
Fig. 4 is the enlarged diagram of " B " in Fig. 3.
Shown in figure: 1, pump chamber, 1.1, the first Sealing, 1.2, the second Sealing, 1.3, seal ring, 2, eccentric hoop, 2.1, straight pin, 2.2, extension arm, 3, rotor, 4, pilot valve, 4.1, valve body, 4.1.1, the first hydraulic fluid port, 4.1.2, the second hydraulic fluid port, 4.1.3, the 3rd hydraulic fluid port, 4.1.4, unloading port, 4.1.5, the first chamfering, 4.1.6, the 4th hydraulic fluid port, 4.2, spool, 4.2.1, the first hydraulic pressure cavity, 4.2.2, the second hydraulic pressure cavity, 4.2.3, the 3rd hydraulic pressure cavity, 4.2.4, containing groove, 4.2.5, the second chamfering, 4.3, preloading spring, 5, oil pipe, 5.1, main hydraulic fluid port, 6, emission reduction chamber, 7, increase displacement chamber, 8, Returnning spring, 9, elastic force controlling device, 9.1, boss, 10, solenoid valve.
Embodiment
Below in conjunction with the drawings and specific embodiments, the utility model is described in further detail.
As depicted in figs. 1 and 2, variable displacement vane pump of the present utility model, comprises the eccentric hoop 2 be located in described pump chamber 1, with the rotor 3 of the inner chamber eccentric setting of described eccentric hoop 2 with for regulating the controlling mechanism of described eccentric hoop 2 and rotor 3 eccentric distances.The eccentric setting that this place refers to refers to that the geometrical center of described eccentric hoop 2 inner chambers does not overlap with the axis of rotor, therefore the blade that sub 3 axis that rotate circumferentially arrange is divided into eccentric hoop 2 inner chambers some cavitys of different volumes, thus in the time that rotor 3 drives blade rotation, between its different cavitys, ceaselessly compress and expand, the size of described eccentric distance has determined the volume difference between different cavitys, and therefore the degree of larger its compression of eccentric distance and expansion is larger.Between one side of the outer circle wall of described eccentric hoop 2 and the inwall of pump chamber 1, by straight pin 2.1 chain connections, its opposite side is provided with extension arm 2.2.Can realize the swing of eccentric hoop 2 by straight pin 2.1, therefore also just can change throw of eccentric, change thus the degree of fluid compression and expansion, realize the variation of fluid discharge capacity.Described variable displacement vane pump also comprises for driving controlling mechanism to make eccentric hoop 2 and the pilot valve 4 that the eccentric distance of rotor 3 changes, between described pilot valve 4 and controlling mechanism, is connected by oil pipe 5.The pilot valve 4 that this place is stated drives described controlling mechanism to refer to, each oil outlet and controlling mechanism oil pocket separately by pilot valve 4 are connected, thus, the connection of the each hydraulic fluid port by pilot valve from disconnect the different cavitys of regulating and controlling mechanism have oil work and without oily off-load.
Described, the swing process of controlling mechanism control eccentric hoop 2 realizes by emission reduction chamber 6, increasing displacement chamber 7 and Returnning spring 8, and the contrary side with respect to rotor 3 eccentric positions of described extension arm 2.2 is located in described emission reduction chamber 6.Certainly the effect of displacement chamber 6 is for oil pump capacity being reduced, namely reducing the eccentric distance between rotor 3 and eccentric hoop 2, the below that therefore described emission reduction chamber 6 is located in Fig. 2, and described rotor is on the upper side compared with the geometrical center of eccentric hoop 2 in Fig. 2.And described emission reduction chamber by the first Sealing 1.1, be located at seal ring 1.3, eccentric hoop 2 sidewalls and pump chamber 1 inwall on straight pin 2.1 and surround the cavity of a sealing.Described increasing displacement chamber 7 is located at a side contrary with emission reduction chamber 6 on described extension arm 2.2, and by the second Sealing 1.2, be located at seal ring 1.3, eccentric hoop 2 sidewalls and pump chamber 1 inwall on straight pin 2.1 and surround the cavity of sealing, described Returnning spring 8 is located in described increasing displacement chamber 7 and its one end is resisted against on described extension arm 2.2, and its other end is resisted against on pump chamber 1 inwall.Owing to having had emission reduction chamber 6 and having increased displacement chamber 7, therefore the Returnning spring 8 in the utility model can be selected the spring that rigidity is very little, and its Main Function just plays a reset response, and this is different from conventional variable-displacement pump.In conventional variable-displacement pump, described Returnning spring need to overcome the pressure in emission reduction chamber 6, makes the two maintain a voltage stabilizing output state, that is to say that this Returnning spring 8 not only plays reset response, it or the equilibrant of voltage stabilizing output, therefore it needs the larger of elastic force.More, because of the cavity volume limited space of described installation Returnning spring 8, therefore the decrement of spring is limited, can not select longer spring in order to enough elastic force to be provided, therefore just need to be higher to the rigidity requirement of spring.This has also increased material requirements and the assembling difficulty of spring virtually.And these have all obtained overcoming in the utility model, because the Returnning spring in the utility model 8 does not need to realize balance between two forces with emission reduction chamber 6, in the time of needs equilibrant, only need to increase displacement chamber 7 and inject certain oil pressure and can resist mutually with emission reduction chamber 6, therefore this Returnning spring 8 can be selected the spring of the less elastic force of routine.
As shown in Figure 3, described pilot valve 4 comprises valve body 4.1, be located at the spool that can slide axially 4.2 in described valve body 4.1 and the preloading spring 4.3 for pretension spool 4.2, upwards be provided with the first hydraulic fluid port 4.1.1, the second hydraulic fluid port 4.1.2 and the 4.1.4 of unloading port the week of described valve body 4.1, described spool 4.2 is provided with for being communicated with the first hydraulic fluid port 4.1.1 with the first hydraulic pressure cavity 4.2.1 of the second hydraulic fluid port 4.1.2 with for being communicated with the second hydraulic pressure cavity 4.2.2 of the second hydraulic fluid port 4.1.2 and the 4.1.4 of unloading port.In Fig. 3, the right side of valve body is provided with the first hydraulic fluid port 4.1.1, and the below of described the first hydraulic fluid port 4.1.1 is provided with the second hydraulic fluid port 4.1.2 side by side, and the corresponding opposite side that is positioned at described the second hydraulic fluid port 4.1.2 below is provided with the 4.1.4 of unloading port.In the time that spool 4.2 moves down into extreme lower position, the first hydraulic pressure cavity 4.2.1 is communicated with the first hydraulic fluid port 4.1.1 and the second hydraulic fluid port 4.1.2, described in the time moving on described spool 4.3, the first hydraulic pressure cavity 4.2.1 is only communicated with the first hydraulic fluid port 4.1.1, the second hydraulic fluid port 4.1.2 is connected with the 4.1.4 of unloading port of opposite side by the second hydraulic pressure cavity 4.2.2, thereby makes to increase the fluid off-load in displacement chamber 7.In described valve body 4.1, be also provided with the three hydraulic fluid port 4.1.3 corresponding with spool 4.2 bottoms, certainly described the 3rd hydraulic fluid port 4.1.3 is positioned at the bottom of spool, correspondingly with the 3rd hydraulic fluid port 4.1.3 on described valve body be provided with a cavity volume, thereby make fluid pass through the 3rd hydraulic fluid port 4.1.3 by spool 4.2 jack-up, overcome the elastic force of preloading spring 4.3, realize moving axially of spool 4.2.As preferably, spool 4.2 bottoms that described the 3rd hydraulic fluid port 4.1.3 is corresponding be circumferentially equipped with the second chamfering 4.2.5, described valve body 4.1 is provided with the first chamfering 4.1.5 corresponding with described the second chamfering 4.2.5, and described the first chamfering 4.1.5 angle is greater than the angle of described the second chamfering 4.2.5.Be not difficult to find, when spool 4.2 is during in least significant end position, its end face is by the bottom surface laminating in valve body 4.1 inner chambers, thus in the time that spool 4.2 need to rise, because both ends of the surface are away from a flash, the surface area moment of this end face becomes large, will cause thus oil liquid pressure to the spool fluctuation of 4.2 bottom surface moments.And by two chamferings are set, the two end face is not fitted, therefore just there is not the transient fluctuation of oil liquid pressure yet.
The top of described spool 4.2 is also provided with containing groove 4.2.4, and one end of described preloading spring 4.3 is located in described containing groove 4.2.4, and its other end and valve body 4.1 lean.
The 4th hydraulic fluid port 4.1.6 of described the first hydraulic fluid port 4.1.1, the 3rd hydraulic fluid port 4.1.3 and emission reduction chamber 6 correspondences is all connected with main hydraulic fluid port 5.1 by oil pipe 5, and described the second hydraulic fluid port 4.1.2 is connected with increasing displacement chamber 7.
Between described preloading spring 4.3 and valve body 4.1, be provided with elastic force controlling device 9, between one end of described elastic force controlling device 9 and valve body 4.1, be threaded, its other end is provided with boss 9.1, and one end of the end face of described boss 9.1 and preloading spring 4.3 leans.Can control described boss 9.1 and rise or decline by screwing elastic force controlling device, thereby can change the pretightening force of preloading spring, can regulate the voltage stabilizing value at steady oil transportation place.
Described variable displacement vane pump also comprises solenoid valve 10, described spool 4.2 is provided with the 3rd hydraulic pressure cavity 4.2.3 that makes spool 4.2 overcome preloading spring 4.3, described solenoid valve 10 is connected with main hydraulic fluid port 5.1 and the 3rd hydraulic pressure cavity 4.2.3 respectively, and described solenoid valve 10 is electrically connected with control system.
Working principle of the present utility model is such: need set solid amount when work when oil liquid pressure is less, oil liquid pressure in described the 3rd hydraulic fluid port 4.1.3 is less than the pretightening force of preloading spring 4.3, therefore spool 4.2 is positioned at extreme lower position, the first hydraulic pressure cavity 4.2.1 is communicated with the first hydraulic fluid port 4.1.1 and the second hydraulic fluid port 4.1.2, making to increase displacement chamber 7 is connected with main hydraulic fluid port 5.1, therefore increasing displacement chamber 7 offsets with the oil liquid pressure in emission reduction chamber 6, under the effect of Returnning spring 8, eccentric hoop 2 is in displacement.When oil liquid pressure is excessive when exceeding the pretightening force of preloading spring 4.3, oil liquid pressure in described the 3rd hydraulic fluid port 4.1.3 acts on the bottom of spool 4.2, thereby the elastic force that makes spool 4.2 overcome preloading spring 4.3 rises, make thus to move with the second hydraulic fluid port 4.1.2 and disconnect on the first hydraulic pressure cavity 4.2.1, make in addition to move and be communicated with the 4.1.4 of unloading port and the second hydraulic fluid port 4.1.2 on the second hydraulic pressure cavity 4.2.2, thereby making to increase displacement chamber 7 is communicated with the 4.1.4 of unloading port, oil liquid pressure off-load therefore makes eccentric hoop 2 swing and reduces discharge capacity output under the pressure-acting in emission reduction chamber 6.Final discharge capacity is stabilized in a steady state value output.
Similarly, in the time setting up solenoid valve 10, by controlling the folding of solenoid valve 10, the climbing power of regulating action that can be artificial on spool 4.2, therefore can realize oil liquid pressure in another steady state value output.
In addition, the corresponding hydraulic fluid port of the described pilot valve of mentioning in the utility model and the cavity of controlling mechanism are connected with main hydraulic fluid port, its objective is and provide a hydraulic power supply for described controlling mechanism, therefore, the fluid source of described main hydraulic fluid port is not only confined to main oil gallery, and it can also be the oil outlet of oil pump.
The foregoing is only preferred embodiment of the present utility model, not for limiting protection domain of the present utility model.All within spirit of the present utility model and principle, any modification of doing, be equal to and replace and improvement etc., within all should being included in protection domain of the present utility model.
Claims (7)
1. a variable displacement vane pump, comprise the eccentric hoop (2) of being located in pump chamber (1), with the rotor (3) of the inner chamber eccentric setting of described eccentric hoop (2) with for regulating the controlling mechanism of described eccentric hoop (2) and rotor (3) eccentric distance, between the inwall of one side of the outer circle wall of described eccentric hoop (2) and pump chamber (1), pass through straight pin (2.1) chain connection, its opposite side is provided with extension arm (2.2), it is characterized in that: described variable displacement vane pump also comprises the pilot valve (4) for driving controlling mechanism that eccentric hoop (2) and the eccentric distance of rotor (3) are changed, between described pilot valve (4) and controlling mechanism, be connected by oil pipe (5).
2. variable displacement vane pump according to claim 1, it is characterized in that: described controlling mechanism comprises emission reduction chamber (6), increase displacement chamber (7) and Returnning spring (8), the contrary side with respect to rotor (3) eccentric position of described extension arm (2.2) is located in described emission reduction chamber (6), by the first Sealing (1.1), be located at the seal ring (1.3) on straight pin (2.1), eccentric hoop (2) sidewall and pump chamber (1) inwall surround, described increasing displacement chamber (7) is located at the upper side contrary with emission reduction chamber (6) of described extension arm (2.2), and by the second Sealing (1.2), be located at the seal ring (1.3) on straight pin (2.1), eccentric hoop (2) sidewall and pump chamber (1) inwall surround, described Returnning spring (8) is located in described increasing displacement chamber (7) and its one end is resisted against on described extension arm (2.2), its the other end is resisted against on pump chamber (1) inwall.
3. variable displacement vane pump according to claim 2, it is characterized in that: described pilot valve (4) comprises valve body (4.1), be located at the interior spool that can slide axially (4.2) of described valve body (4.1) and the preloading spring (4.3) for pretension spool (4.2), the week of described valve body (4.1) is upwards provided with the first hydraulic fluid port (4.1.1), the second hydraulic fluid port (4.1.2) and unloading port (4.1.4), described spool (4.2) is provided with for being communicated with the first hydraulic fluid port (4.1.1) with first hydraulic pressure cavity (4.2.1) of the second hydraulic fluid port (4.1.2) with for being communicated with second hydraulic pressure cavity (4.2.2) of the second hydraulic fluid port (4.1.2) and unloading port (4.1.4), in described valve body (4.1), be also provided with three hydraulic fluid port (4.1.3) corresponding with spool (4.2) bottom, the top of described spool (4.2) is also provided with containing groove (4.2.4), one end of described preloading spring (4.3) is located in described containing groove (4.2.4), its the other end and valve body (4.1) lean.
4. variable displacement vane pump according to claim 3, it is characterized in that: spool (4.2) bottom that described the 3rd hydraulic fluid port (4.1.3) is corresponding be circumferentially equipped with the second chamfering (4.2.5), described valve body (4.1) is provided with first chamfering (4.1.5) corresponding with described the second chamfering (4.2.5), and described the first chamfering (4.1.5) angle is greater than the angle of described the second chamfering (4.2.5).
5. variable displacement vane pump according to claim 3, it is characterized in that: described the first hydraulic fluid port (4.1.1), the 3rd hydraulic fluid port (4.1.3) and the 4th hydraulic fluid port (4.1.6) corresponding to emission reduction chamber (6) are all connected with main hydraulic fluid port (5.1) by oil pipe (5), and described the second hydraulic fluid port (4.1.2) is connected with increasing displacement chamber (7).
6. variable displacement vane pump according to claim 3, it is characterized in that: between described preloading spring (4.3) and valve body (4.1), be provided with elastic force controlling device (9), between one end of described elastic force controlling device (9) and valve body (4.1), be threaded, its the other end is provided with boss (9.1), and one end of the end face of described boss (9.1) and preloading spring (4.3) leans.
7. variable displacement vane pump according to claim 3, it is characterized in that: described variable displacement vane pump also comprises solenoid valve (10), described spool (4.2) is provided with the 3rd hydraulic pressure cavity (4.2.3) that makes spool (4.2) overcome preloading spring (4.3), described solenoid valve (10) is connected with main hydraulic fluid port (5.1) and the 3rd hydraulic pressure cavity (4.2.3) respectively, and described solenoid valve (10) is electrically connected with control system.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201320796601.9U CN203655624U (en) | 2013-12-05 | 2013-12-05 | Variable displacement vane pump |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201320796601.9U CN203655624U (en) | 2013-12-05 | 2013-12-05 | Variable displacement vane pump |
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| Publication Number | Publication Date |
|---|---|
| CN203655624U true CN203655624U (en) | 2014-06-18 |
Family
ID=50922017
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201320796601.9U Withdrawn - After Issue CN203655624U (en) | 2013-12-05 | 2013-12-05 | Variable displacement vane pump |
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| CN (1) | CN203655624U (en) |
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103671093A (en) * | 2013-12-05 | 2014-03-26 | 宁波圣龙汽车动力***股份有限公司 | Displacement-variable impeller pump |
| CN105134589A (en) * | 2015-09-01 | 2015-12-09 | 芜湖德孚转向***有限公司 | Stator assembly capable of changing pump displacement |
| CN105351028A (en) * | 2015-11-04 | 2016-02-24 | 湖南机油泵股份有限公司 | Primary variable displacement vane pump |
| CN106870359A (en) * | 2015-12-11 | 2017-06-20 | 施瓦本冶金工程汽车有限公司 | Pump with adjustable delivery volume |
-
2013
- 2013-12-05 CN CN201320796601.9U patent/CN203655624U/en not_active Withdrawn - After Issue
Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103671093A (en) * | 2013-12-05 | 2014-03-26 | 宁波圣龙汽车动力***股份有限公司 | Displacement-variable impeller pump |
| CN103671093B (en) * | 2013-12-05 | 2016-03-09 | 宁波圣龙汽车动力***股份有限公司 | A kind of variable displacement vane pump |
| CN105134589A (en) * | 2015-09-01 | 2015-12-09 | 芜湖德孚转向***有限公司 | Stator assembly capable of changing pump displacement |
| CN105351028A (en) * | 2015-11-04 | 2016-02-24 | 湖南机油泵股份有限公司 | Primary variable displacement vane pump |
| CN106870359A (en) * | 2015-12-11 | 2017-06-20 | 施瓦本冶金工程汽车有限公司 | Pump with adjustable delivery volume |
| CN106870359B (en) * | 2015-12-11 | 2020-07-10 | 施瓦本冶金工程汽车有限公司 | Pump with adjustable delivery volume |
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