CN211874726U - Floating side plate for counteracting partial radial force by trapped oil force - Google Patents
Floating side plate for counteracting partial radial force by trapped oil force Download PDFInfo
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- CN211874726U CN211874726U CN202020102367.5U CN202020102367U CN211874726U CN 211874726 U CN211874726 U CN 211874726U CN 202020102367 U CN202020102367 U CN 202020102367U CN 211874726 U CN211874726 U CN 211874726U
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Abstract
The utility model discloses an utilize stagnant oil power to offset partial radial force's unsteady curb plate, a serial communication port, including leading oil groove, splayed off-load groove, circular off-load groove, it establishes at unsteady curb plate medial surface to lead the oil groove, the splayed off-load groove is established in the oil inlet side, circular off-load groove is established in the side of producing oil, and this structure can provide enough big oil inlet side off-load area and less and suitable oil outlet side off-load area, and enough big oil inlet side off-load area can guarantee that the oil inlet side is stagnant oil and is fully filled, avoids the emergence of cavitation; the small and proper unloading area of the oil outlet side can promote the high pressure peak value of trapped oil on the oil outlet side to reach the optimal state, thereby realizing partial balance of the radial force of the pump; and the two types of unloading grooves have simple shapes, small processing amount and simple process.
Description
Technical Field
The utility model relates to an external gear pump field, the field is offset to the radial power of concretely relates to external gear pump, and more specifically relates to an utilize trapped oil power to offset the curb plate that floats of partial radial power.
Background
The external gear pump is a power tool for pumping working oil, and has the advantages of price, reliability, service life, self-absorption capacity and the like, so that the external gear pump is quite wide in application. However, the oil trapping phenomenon (including cavitation) and the radial force determined by the structure thereof are seriously damaged, which mainly include that the radial impact force and the inherent radial force caused by the high pressure peak value in the oil trapping compression area cause the damage of the lubricating performance between the bearings together, and the cavitation caused by the low pressure valley value in the oil trapping expansion area is more serious along with the increase of the rotating speed, thereby hindering the further development of the high speed pump. At present, the understanding of trapped oil (pressure) force and radial force is "negative", and are controlled in independent structural modes. Therefore, the utility model provides a reconsider the trapped oil (pressure) force from "the front", and make full use of the high trapped oil force of trapped oil high pressure from the structure, realize the partial balance of inherent radial force, thus improve the bearing lubrication performance and prolong the service life; and the oil trapping low pressure valley value is larger than the rated cavitation pressure of the medium, so that the cavitation-free performance requirement of the gear pump is met.
SUMMERY OF THE UTILITY MODEL
The utility model discloses an utilize trapped oil power to offset partial radial force's curb plate that floats, aim at to improve bearing lubrication performance, increase of service life and realize the no air pocket performance requirement of gear pump.
In order to achieve the expected purpose, the technical scheme adopted by the utility model is as follows:
the floating side plate capable of offsetting partial radial force by using the trapped oil force is characterized by comprising an oil guide groove, a splayed unloading groove and a circular unloading groove, wherein the oil guide groove is formed in the inner side surface of the floating side plate, the splayed unloading groove is formed in the oil inlet side, and the circular unloading groove is formed in the oil outlet side.
Preferably, the splayed unloading grooves are a pair of annular arc unloading grooves symmetrically distributed on the oil inlet side, and each annular arc unloading groove is formed by smoothly connecting an inner arc and an outer arc which take the wheel center as the center of a circle, and a near transition arc and a far transition arc from head to tail.
Preferably, the theoretical positions of the splayed unloading groove are as follows: the inner circular arc of the annular arc unloading groove is superposed with the root circle of the gear on the side, the outer circular arc is tangent to the top circle of the gear on the other side and deviates outwards, and the tooth profile corresponding to the gear on the side is at the position of the minimum trapped oil after the near-transition circular arc is circumscribed.
Preferably, the theoretical position of the splayed unloading groove translates in the oil outlet direction by a first offset distance to form the actual position of the splayed unloading groove.
Preferably, the theoretical positions of the circular unloading groove are as follows: the circular profile of the circular unloading groove is tangent to the root circles of the driving gear and the driven gear respectively and passes through a side clearance point.
Preferably, the theoretical position of the circular unloading groove is translated along the oil outlet direction by a second offset distance to form the actual position of the circular unloading groove.
Has the advantages that: the structure can provide a large enough unloading area at the oil inlet side and a small and proper unloading area at the oil outlet side, and the large enough unloading area at the oil inlet side can ensure that trapped oil at the oil inlet side is fully filled, thereby avoiding the occurrence of cavitation; the small and proper unloading area of the oil outlet side can promote the high pressure peak value of trapped oil on the oil outlet side to reach the optimal state, thereby realizing partial balance of the radial force of the pump; and the two types of unloading grooves have simple shapes, small processing amount and simple process.
Drawings
Fig. 1 is a perspective view.
Fig. 2 is a view showing an inner side surface structure of the floating side plate.
Fig. 3 is a schematic view of the arrangement of the balance structure and the size.
FIG. 4 is a schematic illustration of the partial balancing of trapped oil pressure of radial forces on the driven shaft.
FIG. 5 is a graphical representation of radial force on the driven shaft as a function of trapped oil pressure.
Wherein: 1. the oil guide groove 2, the splayed unloading groove 3, the circular unloading groove 4, the inner side surface 5 of the floating side plate, the outer side surface 6 of the floating side plate, the inner arc 7, the outer arc 8, the middle part A of the floating side plate, the upper end B, the lower end C, the oil inlet side D and the oil outlet side.
Detailed Description
The technical solutions in the embodiments of the present invention will be described clearly and completely with reference to the accompanying drawings in the embodiments of the present invention, and it is obvious that the described embodiments are only some embodiments of the present invention, not all embodiments.
As shown in fig. 1 to 5, a floating side plate for canceling a part of radial force by using trapping force is characterized by comprising an oil guide groove 1, a splayed unloading groove 2 and a circular unloading groove 3. The splayed unloading grooves 2 are a pair of annular arc unloading grooves symmetrically distributed on the oil inlet side C, and each annular arc unloading groove is formed by smoothly connecting an inner arc 6 and an outer arc 7 which take a wheel center as a circle center and a near transition arc and a far transition arc in an end-to-end manner. The theoretical positions of the splayed unloading groove 2 are as follows: the inner arc 6 of the annular arc unloading groove is superposed with the root circle of the gear at the side, the outer arc 7 is tangent to the top circle of the gear at the other side and deviates outwards, and the corresponding tooth profile of the gear at the side is at the position of the close transition arc circumscribed with the minimum trapped oil. The theoretical position of the splayed unloading groove 2 is translated along the oil outlet direction by a first offset distance to form the actual position of the splayed unloading groove 2. The theoretical positions of the circular unloading groove 3 are as follows: the circular profile of the circular unloading groove 3 is tangent to the root circles of the driving gear and the driven gear respectively and passes through a side clearance point. Preferably, the theoretical position of the circular unloading groove 3 is translated along the oil outlet direction by a second offset distance to form the actual position of the circular unloading groove 3. The oil guide groove 1 is arranged on the inner side surface 4 of the floating side plate, the splayed unloading groove 2 is arranged on the oil inlet side C, and the circular unloading groove 3 is arranged on the oil outlet side D.
The specific design principle is as follows:
the main design difficulty of the present invention is how to determine the actual positions of the splayed unloading slot 2 and the circular unloading slot 3, that is, the specific values of the first offset and the second offset Δ.
Step one, the theoretical position of the splayed unloading groove 2 and the theoretical position of the circular unloading groove 3 should meet the following conditions: the splayed unloading grooves 2 are a pair of annular arc unloading grooves symmetrically distributed on the oil inlet side C, and each annular arc unloading groove is formed by a wheelThe inner arc 6 and the outer arc 7 with the center as the center of a circle, and 4 sections of the near transition arc and the far transition arc which are smoothly connected end to end. The theoretical position of each ring arc unloading groove is that an inner arc 6 of each ring arc unloading groove is superposed with a root circle of the gear on the side, an outer arc 7 of each ring arc unloading groove is tangent to a top circle of the gear on the other side and is outwards biased by 1 mm, the corresponding tooth profile of the gear on the side is at the position with minimum oil trapping when the near transition arc is externally tangent, and the corresponding arc center included angle is larger than 240 degreesz，zIs the number of teeth. Wherein, the minimum trapped oil level is the driving gear (the wheel center iso 1) Symmetrical axis and driven wheel groove (wheel center iso 2) The position where the axes of symmetry coincide.
And step two, the circular unloading groove 3 is in a theoretical position that the circular outline is respectively tangent with root circles of the driving gear and the driven gear and passes through a side clearance point m. Wherein the side clearance pointmAs a point of engagementnAbout the centre lineo 1 o 2As shown in fig. 1 and 2.
And step three, analyzing the pressure of the medium on the driven wheel, wherein the radial force on the driven wheel is larger than that on the driving wheel, so that the radial force on the driven wheel is partially balanced.
FIG. 4 depicts the minimum trapped oil position of the gear pair, which is also the trapped oil pressure, biased toward the driven wheel sidep t Is located in the vicinity of the location of the maximum peak.
In a counterclockwise direction of rotation and about the center lineo 1 o 2Is 0°Of driven gear teeth on the starting side [0 ]°,360°]On the tip circle, there is a low pressure depending on the different distribution of the pressure of the mediumeaTransition ofacHigh voltage, high voltagecdAnd trapped oildeFour segments of (1), corresponding to the wheel centero 2Respectively are marked asφ i 、φ m 、φ o Andφ t . Wherein
Where α' is the pitch circle mesh angle, atan () is the arctangent function, and tan () is the tangent function.
To simplify the calculation, the ac section of the transition zone is divided into two sections from the middle position, a low-pressure ab section and a high-pressure bc section. Then, the driven wheel is at [0 degree, 360 degree ]]Addendum circle, which is divided into a low pressure eb section, a high pressure bd section and an oil trapping de section, and the region angles corresponding to the wheel center o2 are phi i +0.5 phi m, 0.5 phi m + phi o and phi t respectively; the pressure of the medium on the tooth top of each section generates the acting force ofF i 、F o AndF t 。
shown in FIG. 4xo 2 yUnder the condition of the coordinate system,F i equivalent to being at the edgeebAnd tooth widthbThe force on the rectangular plate;F o equivalent to being at the edgedbAnd tooth widthbThe force on the rectangular plate;F t equivalent to being at the edgedeAnd tooth widthbThe force on the rectangular plate; the specific calculation is as follows
In the formula (I), the compound is shown in the specification,p i is the oil inlet pressure;p o is the oil outlet pressure;p t is the trapped oil pressure;r a the addendum circle radius.
Step four, analyzing the radial force on the driven shaft: calculating according to the second step to obtain the medium acting force on the driven shaftx、yComponent on axisF px 、F py Is composed of
In fig. 4, due to trapped oil pressure in the trapped oil zonep t The area of action on the driven wheel being about the centre lineo 1 o 2Symmetrical, so trapped oil pressurep t To engagement forceF n There is no effect. Is provided withrIs the reference circle radius;r'is the pitch circle radius. Therefore, it is made of
The driven shaft is subjected to the engaging forcex、yComponent on axisF nx 、F ny Is composed of
Then, the radial force Fr on the driven shaft and the components Frx, Fry thereof on the x and y axes are
Step five, optimizing and adjusting the pump tooth profile parameters: according to radial forceF r And (4) calculating a partial balance index of the peak value and the third step, and carrying out appropriate optimization adjustment on the tooth profile parameters on the premise of not sacrificing the performance index of the unit displacement volume of the pump so as to meet the requirement of partial balance of radial force on the driven shaft.
Sixthly, confirming the actual position of the splayed unloading groove 2 and the actual position of the circular unloading groove 3 which meet the requirements: according to radial forceF r Calculating the optimal high pressure peak of trapped oil on the oil outlet side D by the formula (3) through the partial balance index of the peak value and the adjustment result, and further calculating the required unloading area of the oil outlet side D and the corresponding first offset distance. The oil inlet side C trapped oil low pressure valley has no air pocket performance requirement, and the required oil inlet side C unloading area and the corresponding second offset distance are calculatedΔ。
Example (b): the small side clearance and oil inlet side C2 teeth seal part of the balance structure of the gear pump.
The design requirement is as follows: the rated oil outlet pressure is 3 MPa, the oil inlet pressure is 0.1 MPa, the rated flow is 18L/min, the rated rotation speed is 1500 r/min, the medium viscosity is 0.09 Pa.s, and the rated minimum volume fraction is 95%.
Original parameters: the radial clearance is 0.08 mm, the axial clearance is 0.04 mm, the crest clearance coefficient is 0.25, the pressure angle is 20 degrees, the modulus is 4.5, the tooth number is 8, the tooth crest height coefficient is 1.1476, the deflection coefficient is 0.5079, and the tooth width is 10.65 mm. The transition area starts at an angle of 40 degrees and ends at an angle of 130 degrees, namely, the oil inlet side C2 tooth sealing is adopted.
The radial force at the original parameters was 1158.5N when the effect of trapped oil pressure on the radial force was not considered. On the premise of not sacrificing the performance index of unit displacement volume of the pump, the method adopts a modulus of 3, a tooth number of 17, a tooth crest height coefficient of 1.25, a deflection coefficient of-0.081 and a tooth width of 10.29 mm; the initial angle of the transition area is 40 degrees, the terminal angle of the transition area is 80 degrees, namely the original small radial and large axial geometric dimension of the gear for the pump is adjusted to be the large radial and small axial geometric dimension.
Calculated by the formulas (2) to (6) to obtainp t The radial force under the condition of = 6MPa is 816.7N, and the amplitude reduction reaches 29.5%;p t the radial force at 16.36MPa is 623.9N, the amplitude reduction reaches 46.15%, and the radial force is at the momentxComponent force in the axial directionF rx And =0. It can be seen that the essence of the balance is to compensate the oil inlet side C with the oil trapping force of the portion hatched in FIG. 4xLack of directional medium forces.
The radial force varies with trapped oil pressure as shown in FIG. 5. Wherein the content of the first and second substances,p t =16.36MPa is the optimum high pressure peak of trapped oil, and is based on "optimum high pressure peak of trapped oil → small and appropriate relief area → first offset distance"and" no air pocket requirement (low pressure valley of trapped oil ≥ sp i /3) → sufficiently large relief area → second offset distanceΔ"calculation flow and related formula, and inverse calculation=0.32 mm andΔ=0.56 mm。
in summary, in the case that the specific values in the embodiment are conditional, it is only necessary to translate the splayed unloading groove 2 in the oil outlet direction=0.32 mm, the circular unloading groove 3 is translated along the oil outlet directionΔ=0.56 mm, the design requirements can be met.
To sum up, the utility model discloses reach anticipated purpose.
Claims (6)
1. The floating side plate capable of offsetting partial radial force by using the trapped oil force is characterized by comprising an oil guide groove, a splayed unloading groove and a circular unloading groove, wherein the oil guide groove is formed in the inner side surface of the floating side plate, the splayed unloading groove is formed in the oil inlet side, and the circular unloading groove is formed in the oil outlet side.
2. The floating side plate for counteracting partial radial force by using trapped oil as claimed in claim 1, wherein said splayed unloading slots are a pair of annular arc unloading slots symmetrically distributed on the oil inlet side, and each annular arc unloading slot is composed of an inner arc and an outer arc with the center of a wheel as the center, and the smooth connection of the head and the tail of the near transition arc and the far transition arc.
3. The floating side plate for counteracting part of the radial force by using the trapping force as claimed in claim 2, wherein the theoretical positions of the splayed unloading grooves are as follows: the inner circular arc of the annular arc unloading groove is superposed with the root circle of the gear on the side, the outer circular arc is tangent to the top circle of the gear on the other side and deviates outwards, and the tooth profile corresponding to the gear on the side is at the position of the minimum trapped oil after the near-transition circular arc is circumscribed.
4. The floating side plate for counteracting a portion of radial force using trapping force of oil as claimed in claim 3, wherein said theoretical position of said splayed relief groove is translated in the direction of oil discharge by a first offset distance to form the actual position of said splayed relief groove.
5. The floating side plate for counteracting part of the radial force with trapping force as claimed in claim 1 wherein the theoretical positions of the circular relief grooves are: the circular profile of the circular unloading groove is tangent to the root circles of the driving gear and the driven gear respectively and passes through a side clearance point.
6. The floating side plate for counteracting a portion of the radial force with oil trapping force of claim 5 wherein the theoretical position of the circular relief groove is translated in the oil discharge direction by a second offset distance to form the actual position of the circular relief groove.
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Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
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| CN111059048A (en) * | 2020-01-17 | 2020-04-24 | 宿迁学院 | Floating side plate for counteracting partial radial force by trapped oil force |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN111059048A (en) * | 2020-01-17 | 2020-04-24 | 宿迁学院 | Floating side plate for counteracting partial radial force by trapped oil force |
| CN111059048B (en) * | 2020-01-17 | 2023-11-10 | 宿迁学院 | Floating side plate for counteracting partial radial force by utilizing trapped oil force |
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Effective date of registration: 20211220 Address after: 641400 No. 8, longhui Road, Jiancheng, Jianyang, Chengdu, Sichuan Patentee after: SICHUAN WUHUAN PETROCHEMICAL EQUIPMENT Co.,Ltd. Address before: 223800 South Huanghe Road, Suqian City, Jiangsu Province, 399 Patentee before: SUQIAN College |