CN201818497U - Automotive hydraulic steering pump with dual stators and dual valve bodies - Google Patents
Automotive hydraulic steering pump with dual stators and dual valve bodies Download PDFInfo
- Publication number
- CN201818497U CN201818497U CN2010205084551U CN201020508455U CN201818497U CN 201818497 U CN201818497 U CN 201818497U CN 2010205084551 U CN2010205084551 U CN 2010205084551U CN 201020508455 U CN201020508455 U CN 201020508455U CN 201818497 U CN201818497 U CN 201818497U
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Abstract
The utility model discloses an automotive hydraulic steering pump with dual stators and dual valve bodies, comprising a pump body, a pump cover with a frontally-assembled oil pan structure, a pump shaft, a middle-assembled oil pan, a rear-assembled oil pan, a first stator and rotor vane component, a second stator and rotor vane component and a valve component, wherein the pump cover, the first stator and rotor vane component, the middle-assembled oil pan, the second stator and rotor vane component and a rear-assembled oil pan are sequentially arranged in series on the pump shaft and are subsequently arranged in the pump body, thus forming a chamber A and a chamber B between the components and the pump body; the valve component comprises a C runner hole, two valve holes, a large valve body and a small valve body; the two valve holes are internally provided with a large valve body and a small valve body; the C runner hole is communicated with the chamber A; and the bottoms of the two valve holes are communicated with the chamber B. In the utility model, the structure with dual stators and dual valve bodies is adopted, when the overflow holes have the same area, the overflow quantity is reduced, and the flowing speed is naturally reduced; compared with the single overflow hole, the overflow heating quantity is reduced greatly; the oil temperature of the system is reduced, the reliability of the steering pump is improved; and the service life can be prolonged.
Description
[technical field]
The utility model relates to automobile steering system hydraulic power-assisted steering pump, relates in particular to the hydraulic power-assisted steering pump that adopts two stator double body structures.
[background technique]
Along with developing rapidly of Domestic Automotive Industry, the travelling comfort that people get up to the performance and the driving of automobile requires more and more higher.Recent years particularly, the load-carrying of bridge constructions before large-tonnage is two, mining and engineering is more and more with automobile demand, because the load-carrying of automobile increases, the moment that the driving vehicle front turns to constantly increases, and this just needs to strengthen the cylinder diameter of steering box, and the flow of demand will increase, simultaneously two propons automobiles have increased servo-cylinder again, also need to increase certain flow, because the increasing of load-carrying, the pressure of system also will increase.Total output flow and the pressure of steering pump when auto idle speed that requires will strengthen and could satisfy the demand that turns to, because motor is considered energy-conservation and environmental protection, the idling of design is all lower, the rotating speed that is delivered to steering pump is just not high yet, and this moment demand flow have bigger, have only the increase turn to pump delivery to meet the demands.Old structure steering pump has only a stator and flow control valve, just have following defective: (1) will increase owing to discharge capacity, be subjected to the restriction of stator space and design, the ratio of the line of apsides of stator curve can not exceed certain value, otherwise cause blade to cut off easily, have only the height that increases stator to increase discharge capacity, but the stator height has increased, the profile tolerance of curved surface and can't reach required precision with the perpendicularity of end face, blade, rotor height also will increase simultaneously, precision is difficult to control, and is very big to the overall performance influence of oil pump, has drawback; (2) after discharge capacity increases, when idling, can satisfy steering box and servo-cylinder input flow rate demand, this moment, flow control valve was not opened overflow, but when high speed, because the flow of steering pump output is a constant flow rate, the original structure steering pump has only a flow control valve and flow-off, this moment, unnecessary flow just passed through a flow control valve from the flow-off overflow, because discharge capacity is bigger, very fast during high speed from the velocity ratio of flow-off overflow, cause oily temperature temperature rise too fast, higher (the engineering truck of the temperature of whole system, mining car oil temperature can reach 100 ℃～140 ℃, mainly is because the oil pump overflow produces idle work, changes into heat, it is too high that circulation causes oil liquid temperature for a long time), Sealing is aging to be accelerated, and causes leakage of oil easily, and the too high kinematical viscosity of fluid that causes of oil temperature sharply reduces, oil pump inner body wearing and tearing aggravation causes reduce greatly the working life of steering pump.
[model utility content]
The purpose of this utility model solves the problems of the prior art exactly, proposes the two stator bivalve body power-assisted steering pumps of a kind of automobile hydraulic, can improve the reliability of steering pump, reduces the self-heating amount, increases the service life.
For achieving the above object, the utility model proposes the two stator bivalve body power-assisted steering pumps of a kind of automobile hydraulic, comprise the pump housing, the pump cover of oil distribution casing structure before having, pump shaft, middle oil distribution casing, back oil distribution casing, the first stator rotor blade assembly, the second stator rotor blade assembly, valve assembly, described pump cover, the first stator rotor blade assembly, middle oil distribution casing, the second stator rotor blade assembly, back oil distribution casing is installed in series after on the pump shaft successively, be installed in the pump housing, and form A chamber and B chamber between the pump housing, described valve assembly comprises C runner hole, two valve openings, big valve body and little valve body, be separately installed with big valve body and little valve body in two valve openings, described C runner hole communicates with the A chamber, and the bottom of two valve openings all communicates with the B chamber.
As preferably, be the structure that is connected in parallel between described big valve body and the little valve body.Rational in infrastructure, ingenious.
As preferably, the described first stator rotor blade assembly comprises first stator, be installed in the first rotor on the pump shaft and be located at first blade on the first rotor; The second stator rotor blade assembly comprises second stator, is installed in second rotor on the pump shaft and is located at second epitrochanterian second blade.Simple in structure, cost is low.
As preferably, adopt locating stud to be installed in series between described pump cover, the first stator rotor blade assembly, middle oil distribution casing, the second stator rotor blade assembly, the back oil distribution casing.Simple in structure, easy for installation, cost is low.
As preferably, be provided with spring seat below the described little valve body, on the described spring seat spring is installed, described spring withstands steel ball, makes steel ball withstand little valve body.Reasonable control flow rate, and simple in structure, easy for installation.
The beneficial effects of the utility model: the utility model adopts two stator double body structures, when oil pump in tick-over not during overflow, the whole discharge capacity of oil pump is two stator discharge capacity sums, when high speed operation, 2 all separately overflows of flow that stator produces, because the discharge capacity of single stator is smaller, flow is also smaller when high speed, and the flow of overflow is also just smaller, when the flow-off area is big equally, spillway discharge reduces, flow velocity reduces naturally, compares with single flow-off, has significantly reduced the overflow heating value, the system oil temperature drop is low, has improved the reliability and the working life of steering pump.
Feature of the present utility model and advantage will be elaborated in conjunction with the accompanying drawings by embodiment.
[description of drawings]
Fig. 1 is two stationary part sectional views of the two stator bivalve body power-assisted steering pumps of the utility model automobile hydraulic;
Fig. 2 is the bivalve body portion sectional view of the two stator bivalve body power-assisted steering pumps of the utility model automobile hydraulic;
Fig. 3 is an I place enlarged view among Fig. 2.
[embodiment]
As shown in Figure 1, the two stator bivalve body power-assisted steering pumps of automobile hydraulic, comprise the pump housing 2, the pump cover 1 of oil distribution casing structure before having, pump shaft 12, middle oil distribution casing 6, back oil distribution casing 8, the first stator rotor blade assembly, the second stator rotor blade assembly, valve assembly, described pump cover 1, the first stator rotor blade assembly, middle oil distribution casing 6, the second stator rotor blade assembly, back oil distribution casing 8 is installed in series after on the pump shaft 12 successively, be installed in the pump housing 2, and form A chamber and B chamber between the pump housing 2, described valve assembly comprises C runner hole, two valve openings, big valve body 13 and little valve body 15, be separately installed with big valve body 13 and little valve body 15 in two valve openings, described C runner hole communicates with the A chamber, and the bottom of two valve openings all communicates with the B chamber.The described first stator rotor blade assembly comprises first stator 3, be installed in the first rotor 4 on the pump shaft 12 and be located at first blade 5 on the first rotor 4; The second stator rotor blade assembly comprises second stator 9, be installed in second rotor 10 on the pump shaft 12 and be located at second blade 11 on second rotor 10.Adopt locating stud 7 to be installed in series between described pump cover 1, the first stator rotor blade assembly, middle oil distribution casing 6, the second stator rotor blade assembly, the back oil distribution casing 8.By pump shaft 12 and locating stud 7 pump cover 1 (preceding oil distribution casing structure is as a whole with pump cover), first stator 3, the first rotor 4, middle oil distribution casing 5, second stator 9, second rotor 10 and back oil distribution casing 8 are connected and to fit together, integral body is combined with the pump housing 2 again, form A chamber (fuel-displaced epicoele) and B chamber (fuel-displaced cavity of resorption) two oil extraction districts, C runner hole in the middle of A chamber and the valve opening is connected, the bottom of B chamber and two valve openings is connected, by big valve body 13 and little valve body 15 A chamber and B chamber are separated, this moment, disconnected in two chambeies.
Shown in Fig. 2,3, be the structure that is connected in parallel between described big valve body 13 and the little valve body 15.Described little valve body 15 belows are provided with spring seat 18, on the described spring seat 18 spring 17 are installed, and described spring 17 withstands steel ball 16, make steel ball 16 withstand little valve body 15.
Two stator bivalve body power-assisted steering pump work principles: when the engine-driving steering pump is worked, the oil pump oil extraction of starting working, when the engine speed that drives the steering pump rotation at n
1During with interior work, this moment pump cover 1 and first stator 3, the first rotor 4, the fluid flow that the combination of first blade 5 and middle oil distribution casing 6 is discharged flows to A chamber (on go out oil pocket), the middle oil distribution casing 6 and second stator 9, second rotor 10, the fluid that the combination of second blade 11 and back oil distribution casing 8 is discharged flows to B chamber (going out oil pocket down), this moment since rotating speed in n1, the fluid resistance in B chamber is not enough to overcome the pretightening force of big valve body 13 springs, this moment, big valve body 13 was motionless, first flow-off 19 and second flow-off 20 are sealed fully, this moment, the fluid in A chamber was also sealed, can't be from 19 overflows of first flow-off, fluid can only overcome the resistance of the steel ball 16 following springs 17 in the little valve body 15, the fluid in A chamber flow in the B chamber from this mouth, flow in the steering system by oil outlet again, because big valve body 13 does not produce overflow, the flow of output this moment:
Q＝Q
1+Q
2，
Q
1=q
1* n (flow in A chamber) q
1The discharge capacity of-the first stator 3
Q
2=q
2* n (flow in A chamber) q
2The discharge capacity of-the second stator 9
N-steering pump rotating speed
Because the discharge capacity of this kind structural requirement first stator 3 and second stator 9 must be identical, be again to be connected on the same axle, rotation speed n is also identical, so output flow Q=2q * n, this moment, the discharge capacity of two stators was the relations that add up, the flow of output is bigger naturally, satisfies the vehicle of the big traffic demand of low speed.
When continuing to raise, the rotating speed of motor reaches n
1Or n
1When above, the fluid that is input to the B chamber increases, be subjected to the damping function of damping hole, the liquid resistance in B chamber (fuel-displaced cavity of resorption) increases, the resistance in B chamber is greater than the initial tension of spring of big valve body 13 at this moment, big valve body 13 moves upward, this moment, first flow-off 19 and second flow-off 20 were opened overflow simultaneously, this moment, a part of fluid in A chamber overflowed to the oil suction district by first flow-off 19, part fluid is by overcoming the resistance of the spring 17 under the steel ball 16 in the little valve body 15, pushing little valve port open flows in the B chamber, a part of fluid in the B chamber overflows to the oil suction district by second flow-off 20 at this moment, the fluid that part fluid and A chamber flow into flow in the steering box by oil outlet, keeps the normal demand flow of steering box.Along with the rising that engine speed is not stopped, the flow that steering pump is input to A chamber and B chamber constantly increases, because the specific (special) requirements of steering box, at n
1More than the rotating speed, requiring the flow of steering pump output is the constant current amount, and changes in flow rate is little, and from the also constantly increase of flow of flow-off 1 and flow-off 2 overflows, this moment, the fuel-displaced and spillway discharge of steering pump was following mode:
This moment, the steering pump rotating speed was n
2, n
2〉=n
1, the steering box demand volume is Q, and Q is a steady state value, and first stator 3 is identical with second stator, 9 discharge capacities, so the flow Q in A chamber
1The flow Q in=B chamber
2
The flow in A chamber is: Q
1=q * n
2
The flow in B chamber is: Q
2=q * n
2
Since the flow Q fixed value of oil outlet output, the flow sum of A chamber and B chamber output just, and the A chamber is from the flow Q of flow-off 1 overflow at this moment
3=Q
1-Q/2, the B chamber is from the flow Q of flow-off 2 overflows
4=Q
2-Q/2.For single stator and single valve body structure, (under the equal rotating speed, discharge capacity is 2q, and Q is identical for the oil outlet flow) under the same service condition, the excess flow of single flow-off is Q
3+ Q
4, flow velocity is too fast, causes the fluid temperature rise too fast.And two stator double body structures are divided into 2 identical values (total displacement is constant) to the stator discharge capacity, the discharge capacity of single stator is smaller, the flow that flow into single oil pocket during high speed rotating is also smaller, first flow-off 19 is identical with the excess flow of second flow-off 20, the spillway discharge of 2 flow-offs has only half spillway discharge of single stator single valve body structure, under the same overflow area, the flow velocity of overflow is also just slow, the heating nature of oil pump is just fewer, and experiment confirm is under same service condition, than low about 30 ℃ of single stator single valve body structure, the system oil temperature control is in small range, and the reduction of system oil temperature is to improving greatly the working life of oil pump.
Two stator bivalve body power-assisted steering pump performance parameters:
1. single stator discharge capacity scope: 12～20ml/r
2. pressure range: maximum 16MPa
3. speed range: 500～4000r/min
The foregoing description is to explanation of the present utility model, is not to qualification of the present utility model, any scheme after the utility model simple transformation is all belonged to protection domain of the present utility model.
Claims (5)
1. two stator bivalve body power-assisted steering pumps of automobile hydraulic, it is characterized in that: comprise the pump housing (2), the pump cover (1) of oil distribution casing structure before having, pump shaft (12), middle oil distribution casing (6), back oil distribution casing (8), the first stator rotor blade assembly, the second stator rotor blade assembly, valve assembly, described pump cover (1), the first stator rotor blade assembly, middle oil distribution casing (6), the second stator rotor blade assembly, back oil distribution casing (8) is installed in series successively after pump shaft (12) is gone up, be installed in the pump housing (2), and form A chamber and B chamber between the pump housing (2), described valve assembly comprises C runner hole, two valve openings, big valve body (13) and little valve body (15), be separately installed with big valve body (13) and little valve body (15) in two valve openings, described C runner hole communicates with the A chamber, and the bottom of two valve openings all communicates with the B chamber.
2. the two stator bivalve body power-assisted steering pumps of automobile hydraulic as claimed in claim 1 is characterized in that: be the structure that is connected in parallel between described big valve body (13) and the little valve body (15).
3. the two stator bivalve body power-assisted steering pumps of automobile hydraulic as claimed in claim 1 is characterized in that: the described first stator rotor blade assembly comprises first stator (3), be installed in the first rotor (4) on the pump shaft (12) and be located at first blade (5) on the first rotor (4); The second stator rotor blade assembly comprises second stator (9), be installed in second rotor (10) on the pump shaft (12) and be located at second blade (11) on second rotor (10).
4. the two stator bivalve body power-assisted steering pumps of automobile hydraulic as claimed in claim 1 is characterized in that: adopt locating stud (7) to be installed in series between described pump cover (1), the first stator rotor blade assembly, middle oil distribution casing (6), the second stator rotor blade assembly, the back oil distribution casing (8).
5. as the two stator bivalve body power-assisted steering pumps of each described automobile hydraulic in the claim 1～4, it is characterized in that: described little valve body (15) below is provided with spring seat (18), spring (17) is installed on the described spring seat (18), described spring (17) withstands steel ball (16), makes steel ball (16) withstand little valve body (15).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2010205084551U CN201818497U (en) | 2010-08-24 | 2010-08-24 | Automotive hydraulic steering pump with dual stators and dual valve bodies |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2010205084551U CN201818497U (en) | 2010-08-24 | 2010-08-24 | Automotive hydraulic steering pump with dual stators and dual valve bodies |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN201818497U true CN201818497U (en) | 2011-05-04 |
Family
ID=43916454
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN2010205084551U Expired - Lifetime CN201818497U (en) | 2010-08-24 | 2010-08-24 | Automotive hydraulic steering pump with dual stators and dual valve bodies |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN201818497U (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101949385A (en) * | 2010-08-24 | 2011-01-19 | 全兴精工集团有限公司 | Hydraulic power-assisted steering pump with double stators and double valve bodies for vehicles |
-
2010
- 2010-08-24 CN CN2010205084551U patent/CN201818497U/en not_active Expired - Lifetime
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101949385A (en) * | 2010-08-24 | 2011-01-19 | 全兴精工集团有限公司 | Hydraulic power-assisted steering pump with double stators and double valve bodies for vehicles |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| AV01 | Patent right actively abandoned |
Granted publication date: 20110504 Effective date of abandoning: 20120606 |