CN112664590A - Hydraulic retarder driving wheel blade with oil passage and design method thereof - Google Patents
Hydraulic retarder driving wheel blade with oil passage and design method thereof Download PDFInfo
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Abstract
The invention belongs to the field of structural design of a hydraulic speed reducer and discloses a runner blade with an oil passage of the hydraulic speed reducer and a design method thereof. The impeller wheel is provided with an even number of blades, the blades are divided into common blades and blades with oil passing runners, and the common blades and the blades with the oil passing runners are uniformly distributed at intervals; and each blade with the oil passing flow channel is provided with an oil passing flow channel with a protruding bulge structure, the oil passing flow channel is arranged at the opening of the front surface of the moving wheel and positioned at the middle part of the inner ring and the outer ring of the impeller, the back surface of the blade is partially cut off, and the front surface of the blade is reserved with an entity to form a guard plate structure. The design method comprises the following steps: selecting a blade shape, determining the orientation of a bulge structure designed on an oil passing flow passage blade, designing the shape of the bulge structure of the blade with the oil passing flow passage, and designing an oil hole of the oil passing flow passage; the blades with the oil passing flow passages are distributed at intervals with the common blades. The invention can fully utilize the pumping effect generated by the rotating hydraulic reducer driving wheel, improve the liquid filling speed and further improve the response speed of the hydraulic reducer.
Description
Technical Field
The invention belongs to the field of structural design of a hydraulic speed reducer, and particularly relates to a driving wheel blade with an oil flow passage of the hydraulic speed reducer and a design method thereof.
Background
The hydraulic retarder is a vehicle auxiliary brake which is widely applied at present, is usually assembled on urban buses, trucks and high-grade automobiles, and is mainly used for braking vehicles continuously descending long slopes for a long time.
The hydraulic retarder is a special form of a hydraulic coupler, namely a driving wheel rotates along with a shaft, and a fixed wheel is fixed on a shell. The response speed of the hydraulic retarder is an important performance parameter, and is mainly determined by an oil inlet form and a blade structure.
The invention relates to a hydraulic retarder charging braking process braking torque control method (patent number ZL 201510894049.0) invention point S1 applied by northern China vehicle research institute, and provides a 380 hydraulic retarder design, wherein the patent describes the structure of the hydraulic retarder and the number, thickness and inclination angle of blades in a driving wheel and a fixed wheel. The prior driving wheel oil inlet structure is rough, low in braking capacity and slow in effect taking speed. In order to fully improve the response speed of the hydraulic speed reducer, a new driving wheel blade structure and an optimized driving wheel liquid inlet type hydraulic speed reducer blade structure design need to be developed.
Disclosure of Invention
The invention aims to provide a runner blade structure with an oil flow channel for a hydraulic retarder and a parametric optimization method thereof. By optimizing the structural parameters, the braking capability and the response speed of the brake can be further improved. Provides basis for the design and research of hydraulic retarder products in China.
(II) the invention complete technical scheme
One aspect of the invention provides a hydraulic retarder driving wheel blade with an oil flow passage, wherein the driving wheel blade is provided with an even number of blades, the blades are divided into common blades and blades with the oil flow passage, and the common blades and the blades with the oil flow passage are uniformly distributed at intervals; the blade with the oil passing flow channel is provided with the oil passing flow channel with the protruding bulge structure, the oil passing flow channel is positioned in the middle part of the inner ring and the outer ring of the impeller at the opening on the front surface of the driving wheel, the back surface of the blade is partially cut off, and the entity is reserved on the front surface of the blade to form a guard plate structure so as to assist in forming a low-pressure area and facilitate oil inlet.
Further, the forward inclination angle of the blade with the oil flow passage is 0-45 degrees, and the thickness of the blade is 5-8 mm.
Further, the cross section of the blade bulge structure with the oil passage is respectively designed into a runway shape formed by two sections of large arcs and two sections of small arcs in a tangent mode, the radius of the two sections of large arcs of the top end base body structure is recorded as P3, the value of the radius is in the range of 80-120 mm, the radius of the two sections of small arcs is recorded as P2, the value of the radius is in the range of 3-6 mm, the radius of the two sections of large arcs of the bottom end base body structure is recorded as P6, the value of the radius is in the range of 150-250 mm, and the radius of the two sections of small arcs is P5, the value of the; the center plane of the convex bulge structure on the blade and the plane of the common blade have an offset distance P8, and the offset distance is in the range of 2-6 mm; the connecting line of the centers of the two arcs of the base structure at the top end of the blade with the oil passage and the connecting line of the centers of the two arcs of the base structure at the bottom end of the blade are in the same plane and parallel to the common blade.
Furthermore, the cross section of the oil passing flow passage is in a track shape formed by two sections of semi-arcs and two tangent line sections.
Further, when the outer diameter of the circulating circle of the hydraulic speed reducer is 380mm, the radius P9 of the two semicircular arcs ranges from 3 mm to 6mm, the radius P10 of the two tangential line segments ranges from 10 mm to 15mm, and the included angle P12 between the end face of the removed part of the back of the blade and the edge of the blade ranges from 15 degrees to 20 degrees.
The invention also provides a design method of the runner blade with the oil passage of the hydraulic retarder, which comprises the following steps:
(1) selecting a leaf shape;
selecting a common blade, wherein the common blade is provided with a front rake and a straight blade profile which is modified at the edge of the blade; the forward inclination angle is 0-45 degrees, and the thickness of the blade is 5-8 mm;
(2) determining the orientation of a design bulge structure on the oil passing flow passage blade;
setting the forward inclination angle of the common blade as the forward inclination angle of the blade with the oil flow passage blade, and determining the orientation of the bulge structure of the oil flow passage blade;
(3) designing the bulge structure shape of the blade with the oil passage;
the cross section of the blade bulge structure with the oil passing flow channel is respectively designed into a runway shape formed by two sections of large arcs and two sections of small arcs in a tangent mode, the radius of the two sections of large arcs of the top end base body structure is marked as P3, the value of the radius of the two sections of large arcs is within the range of 80-120 mm, the radius of the two sections of small arcs is marked as P2, the value of the radius of the two sections of small arcs is within the range of 3-6 mm, the radius of the two sections of large arcs of the bottom end base body structure is marked as P6, the value of the two sections of large arcs is within the range of 150-; the center plane of the convex bulge structure on the blade and the plane of the common blade have an offset distance P8, and the offset distance is in the range of 2-6 mm; the connecting line of the centers of the two arcs of the base body structure at the top end of the blade of the oil passing flow passage and the connecting line of the centers of the two arcs of the base body structure at the bottom end of the blade are in the same plane and are parallel to the common blade;
(4) an oil passing flow passage oil hole is designed on the blade bulge structure;
an oil passing flow passage oil hole is designed in a bulge structure on the blade bulge structure, the cross section of the oil passing flow passage oil hole is in a track shape formed by two sections of semi-arcs and two tangent line sections, and the included angle between the axis of an oil passage on the central plane of the oil passing flow passage oil hole and the edge line of the blade is marked as P11;
(5) the oil passing flow channel bulge structure correspondingly cuts the back of the blade at the edge of the blade on the front side of the impeller, reserves the front part of the blade to form a guard plate structure in the figures 1a and 5, and modifies the junction of the base body structure of the bulge structure and the common blade structure with a fillet to ensure that the base body structure and the common blade structure are in smooth transition; the included angle between the end face of the removed part of the back of the blade and the edge of the blade is marked as P12, and the included angle is generally 15-20 degrees;
(6) the blades with the oil passing flow passages are distributed at intervals with the common blades.
Further, when the outer diameter of the circulating circle of the hydraulic speed reducer is 380mm, the radius P9 of the two half circular arcs ranges from 3 mm to 6mm, and the two tangential line sections P10 range from 10 mm to 15 mm.
Further, the method for determining the included angle P11 between the axis of the oil passage on the central plane of the oil hole of the oil passing channel and the edge line of the blade is as follows: the oil passing flow passage is communicated with the front cavity of the impeller and the back oil suction chamber of the impeller, one end opening of the oil passing flow passage is designed at the front end of the impeller and is positioned in the middle of the cavity, and the other end opening of the oil passing flow passage is designed at the back end of the impeller and is positioned at the outer ring part of the oil suction chamber, so that the oil passage angle parameter P11 is determined.
The invention has the beneficial effects that:
the hydraulic retarder has the significance of optimizing the liquid filling effect characteristic of the hydraulic retarder, namely, when the hydraulic retarder is required to provide braking torque, the pump suction effect generated by the rotating driving wheel of the hydraulic retarder can be fully utilized, the liquid filling speed is increased, and the response speed of the hydraulic retarder is further increased. Meanwhile, the parameter optimization is carried out according to the design method of the invention, so that the high-efficiency balance between the response speed and the braking torque can be obtained, and the high braking capacity can be ensured while the required response speed is obtained. The optimal structure obtained by the method of the invention can shorten the onset time by not less than 15% and improve the braking torque by not less than 5% under the same outline size of the driving wheel.
Drawings
FIG. 1 is the shape of a hydraulic retarder driving wheel with oil flow channel blades;
FIG. 2 shows a parameter P1 of a blade with an oil passage: a schematic diagram of the front rake angle of the blade;
FIG. 3 is a schematic diagram of a base structure of a vane with an oil passage and related parameters P2-P8;
FIG. 4 is a schematic view of the blade oil passing channel with the oil passing channel and the relevant parameters P9-P12 of the blade rear side removing structure;
in the figure: p1-blade rake angle; p2-radius of the small arc at the top of the blade bulge structure (process parameters); p3-radius of large circular arc at the top end of the blade bulge structure (process parameter); p4-arc center distance (process parameter) of the top end of the blade bulge structure; p5-radius of the small arc at the top of the blade bulge structure (process parameters); p6-radius of large circular arc at the top end of the blade bulge structure (process parameter); p7-arc center distance (process parameter) of the top end of the blade bulge structure; p8-distance between the central plane of the blade bulge structure and the plane of the common blade; p9-arc radius of oil passage channel of blade; p10 is the arc center distance of the blade oil flow passage; p11-included angle between the oil channel axis and the blade edge line on the central plane of the blade oil channel; p12-included angle between the end face of the removed part of the back of the blade and the edge of the blade;
fig. 5 is a schematic view of a convex bulge on a blade.
Detailed Description
The invention is described in further detail below with reference to the figures and specific examples.
The outline of the hydraulic speed reducer driving wheel with the blade having the oil flow passage according to the present invention is shown in fig. 1. The impeller has 20 blades, 10 common blades (the blade profile is designed by adopting the method in the patent ZL 201510894049.0), and 10 blades with oil passing flow passages are uniformly distributed at intervals. The oil passage is used for increasing the oil filling speed so as to shorten the braking acting time. The opening of the oil passing flow passage on the front surface (one side of the circular cavity) of the driving wheel is positioned in the middle part of the inner ring and the outer ring of the impeller, and the pressure at the position is the lowest according to the flowing rule of oil in the circular cavity, so that oil feeding is facilitated. The rear side surface of the blade is partially cut off so as to fully utilize oil inlet in a low-pressure area and reduce the overflowing resistance of oil when the oil circularly flows between the moving wheel and the fixed wheel; the back of the blade is partially cut off, and the front of the blade is kept with a solid body to form a guard plate structure so as to assist in forming a low-pressure area and facilitate oil feeding.
The invention relates to the structural parameters of the blade and the design method thereof. The size of the circular structure of the hydraulic speed reducer is determined by the integral arrangement, and the invention only relates to design parameters and a method of a blade structure with an oil passing flow channel. The common blade of the driving wheel is a flat plate modification blade with a front rake angle, and the blade with the oil passing flow channel increases the entity based on the common blade structure and provides the oil passing flow channel on the basis of the entity. Therefore, the front rake angle P1 of the blade with the oil passing flow passage has the same value as that of the common blade.
The convex bulge structure shown on the left of fig. 5 below is made from hybrid features on a generic blade basis for machining (direct casting or machining) the oil flow passages. The specific parameters of the matrix structure are shown in fig. 3(b) below. The upper and lower profiles of the mixed characteristic are composed of four sections of circular arcs, the corresponding radiuses of the top profiles are respectively the radius P2 of a small circular arc at the top end of the blade bulge structure and the radius P3 of a large circular arc at the top end of the blade bulge structure, and the center distance of the circular arcs is the center distance P4 of the circular arcs at the top end of the blade bulge structure; the corresponding radiuses of the bottom end profile are respectively a small arc radius P5 at the bottom end of the blade bulge structure and a large arc radius P6 at the bottom end of the blade bulge structure, and the corresponding arc center distance of the small arc radius P5 at the bottom end of the blade bulge structure is the arc center distance P7 at the bottom end of the blade bulge structure; the distance between the central plane of the blade bulge structure and the plane of the common blade is recorded as P8. And (3) determining each radius parameter according to the required oil passing flow passage size, and ensuring the wall thickness of 1.5-2 mm.
The oil passing flow passage is formed by connecting two parallel cylindrical holes, as shown in fig. 4(a), relevant parameters are arc radius P9 of the blade oil passing flow passage, arc center distance P10 of the blade oil passing flow passage, and angle parameter P11 is shown in fig. 4 (b). Fig. 4(b) shows an included angle P11 between the axis of the oil gallery and the edge line of the vane on the central plane of the oil gallery of the vane and an included angle P12 between the end face of the removed part of the back of the vane with the oil gallery and the edge of the vane.
According to the analysis, a hydraulic retarder blade parameterization design method with an oil passing channel is established, 12 parameters from P1 to P12 are formed, and the blade structure is controlled by the parameters. The blade form designed by the method can improve the acting speed by about 10 percent by optimizing parameter selection (by virtue of flow field simulation calculation and test). The formation of the oil passing flow passage is to provide a similar bulge design on the basis of the original common blade so as to provide a base body for the oil passing flow passage. The bulge structure enables the oil passing flow channel to have enough wall thickness and strength on one hand, and on the other hand, the bulge structure can influence the flow of oil in a circulating circle of the impeller of the speed reducer so as to influence the braking torque. The design process optimizes the specific parameter combination through parameter adjustment.
The method comprises the following steps:
(1) selecting a leaf shape;
selecting a method design in a patent ZL201510894049.0 for basic blade profile selection, namely selecting a straight blade profile with a front rake angle and a blade edge modification mode, wherein the front rake angle, the blade thickness and the blade modification mode are all selected from a patent ZL 201510894049.0;
selecting a common blade, wherein the common blade is provided with a front rake and a straight blade profile which is modified at the edge of the blade; the anteversion angle is 0-45 degrees; the thickness is 5-8 mm; the blade modification mode is that a chamfer structure is constructed at the edge of the blade and is in arc transition with the surface of the original blade so as to reduce the edge thickness and further reduce the resistance of liquid circulation flow.
(2) Determining the orientation of a design bulge structure on the oil passing flow passage blade;
setting the forward inclination angle of the common blade as the forward inclination angle P1 of the blade with the oil flow passage, thereby determining the orientation of the bulge structure of the oil flow passage blade;
a three-dimensional modeling software parameterization design method is adopted to obtain a forward rake angle P1 of the blade with the oil passing runner, as shown in figure 2, a parameter P1 determines the orientation of a bulge structure of the blade with the oil passing runner, namely, a connecting line of centers of two arcs of a base structure at the top end of the blade and a connecting line of centers of two arcs of a base structure at the bottom end of the blade are in the same plane and are parallel to a common blade (determined by a forward rake angle of the blade) as shown in figure 3.
(3) Determining the shape of the bulge structure of the oil passing runner blade;
an oil passing flow channel with a convex bulge structure is designed on a common blade to form a blade with the oil passing flow channel, openings at two ends of the oil passing flow channel are respectively arranged at the front end of an impeller and positioned in the middle of a cavity, and the back end of the impeller is positioned at the outer ring part of an oil absorption chamber;
referring to fig. 3, the cross section of the blade with the base structure of the oil passage is respectively designed into a runway shape formed by two sections of large arcs and two sections of small arcs which are tangent, the connecting line of the centers of the two arcs of the base structure at the top end of the blade of the oil passage and the connecting line of the centers of the two arcs of the base structure at the bottom end of the blade are in the same plane and are parallel to a common blade, the size of the base structure at the bottom end of the blade is larger than that of the base structure at the top end, a draft angle is formed on the one hand, and the circular flow resistance of fluid between.
The rudiment shape of the bulge structure of the blade with the oil passage is obtained by adopting a mixed characteristic mode of three-dimensional design software, as shown in figure 3, the top end and the bottom end of the bulge structure are both formed by four sections of circular arcs, two sections of large circular arcs are tangent to two sections of small circular arcs to form a runway shape, in the bulge structure at the top end of the blade, the thickness direction of the blade is formed by two sections of circular arcs with the radius of P2, the distance between the centers of the two circular arcs is P4, the length direction of the blade is formed by two sections of circular arcs with the radius of P3, and the design of the circular arcs forming the bulge outline on the thickness and the length is tangent. Similarly, in the bottom end bulge structure of the blade, the thickness direction of the blade is composed of two arcs with the radius of P5, the center distance of the two arcs is P7, the length direction of the blade is composed of two arcs with the radius of P6, and the thickness is tangent to the arc design forming the bulge outline in the length direction. The size of the base structure at the bottom end of the blade is larger than that of the base structure at the top end of the blade, so that a die drawing angle gradually reduced from the bottom end of the blade to the cross section of the top end of the blade is formed, and demolding is facilitated in casting. The center plane of the convex bulge structure on the blade and the plane of the common blade have an offset distance P8, and the offset distance is used for reducing the influence of the bulge structure on the flow field of the forward tilting direction area of the blade as much as possible, so that the bulge structure is gradually reduced to have adverse effect on the braking torque. The size of the bulge is related to the size of the oil passing channel oil hole in the following (5), the oil passing channel oil hole needs to have the wall thickness not less than 2mm to ensure the strength of the blade, the specific parameter value can be optimized by a CFD flow field simulation prediction mode, and parameters P2-P8 are extracted from a matrix structure.
(4) An oil passing flow passage oil hole is designed on the blade bulge structure;
as shown in fig. 4, the oil passing channel hole is designed in the bulge structure on the blade bulge structure, the cross section of the oil passing channel hole is in a track shape formed by two sections of semi-arcs and two tangent line segments, the radius of the two semi-arcs is marked as P9, the radius of the tangent line segment is marked as P10, the length of the radius of the tangent line segment P10 is equal to the distance between the centers of the two semi-arcs, the oil passing channel area of the oil passage is determined by the arc radius P9 of the blade oil passing channel and the arc center distance P10 of the blade oil passing channel, the larger the value of the oil passing channel area is, namely, the oil filling effect speed is improved, but the bulge structure size is increased if the oil filling effect speed is too high, so that the oil flowing resistance is increased, the braking torque is reduced, taking the external diameter size of a circulating circle of the hydraulic speed reducer in the design as 380mm as an example, the P9 generally takes a value of 3-6 mm, the P10 generally takes a value of 10-15 mm, and the specific value needs to be balanced between the braking torque value and the oil charge acting time in the overall design index of the hydraulic speed reducer; the included angle between the axis of the oil passage on the central plane of the oil passage hole and the edge line of the blade is marked as P11.
(5) The bulge structure of the oil passing flow channel correspondingly cuts off the back of the blade at the edge of the blade at the front of the impeller, the front part of the blade is reserved to form the guard plate structure in the figure 1a, as shown in figure 5, oil is fed in by fully utilizing a low-pressure area, the overflowing resistance of oil circularly flowing between the driving wheel and the fixed wheel is reduced, the oil is conveniently fed in, an oil passage is included in the cut-off, the included angle between the end face of the removed part of the back of the blade and the edge of the blade is marked as P12, and the junction of the base structure of the bulge structure and the common blade structure where the bulge structure is located is modified by a fillet to. The blade forward-tilting direction side, i.e., the impeller rotation direction, is defined as a blade front surface, and the other surface is defined as a blade back surface. The P12 parameter is generally 15-20 °.
(6) The blades with the oil passing flow passages are distributed at intervals with the common blades.
The oil passing flow passage needs to communicate a cavity on the front surface of the impeller (as shown in fig. 1(a)) with an oil suction chamber on the back surface of the impeller (as shown in fig. 1(b)), and the oil passage opening is located in the middle part of the cavity (where the pressure is lowest to facilitate oil suction) at the front surface end of the impeller, and the oil passage opening is located in the outer ring part of the oil suction chamber (to fully utilize the centrifugal force of oil in the oil suction chamber to assist oil suction), which is required to determine the oil passage angle parameter P11.
The above description is only a preferred embodiment of the present invention and is not intended to limit the present invention, and various modifications and changes may be made by those skilled in the art. Any modification, equivalent replacement, or improvement made within the spirit and principle of the present invention should be included in the protection scope of the present invention.
Claims (10)
1. A hydraulic retarder driving wheel blade with an oil passing channel is characterized in that the driving wheel blade wheel is provided with an even number of blades, the blades are divided into common blades and blades with the oil passing channel, and the common blades and the blades with the oil passing channel are uniformly distributed at intervals; the blade with the oil passing flow channel is provided with the oil passing flow channel with the protruding bulge structure, the oil passing flow channel is positioned in the middle part of the inner ring and the outer ring of the impeller at the opening on the front surface of the driving wheel, the back surface of the blade is partially cut off, and the entity is reserved on the front surface of the blade to form a guard plate structure so as to assist in forming a low-pressure area and facilitate oil inlet.
2. A hydrodynamic retarder drive oil flow channel runner blade as claimed in claim 1 wherein said oil flow channel runner blade has a forward pitch angle of 0 to 45 ° and a blade thickness of 5 to 8 mm.
3. The hydrodynamic retarder driving runner blade with the oil passing channel as claimed in claim 2, wherein the cross-sectional shape of the bulge structure with the oil passing channel is respectively designed into a racetrack shape formed by two large arcs and two small arcs which are tangent to each other, the radius of the two large arcs of the top base structure is recorded as P3, the value is within the range of 80-120 mm, the radius of the two small arcs is recorded as P2, the value is within the range of 3-6 mm, the radius of the two large arcs of the bottom base structure is recorded as P6, the value is within the range of 150-250 mm, and the radius of the two small arcs is recorded as P5, the value is within the range of 5-8 mm; the center plane of the convex bulge structure on the blade and the plane of the common blade have an offset distance P8, and the offset distance is in the range of 2-6 mm; the connecting line of the centers of the two arcs of the base structure at the top end of the blade with the oil passage and the connecting line of the centers of the two arcs of the base structure at the bottom end of the blade are in the same plane and parallel to the common blade.
4. A hydrodynamic retarder with an oil flow channel driving wheel vane as claimed in claim 1 wherein said oil flow channel has a cross-sectional shape of a race track formed by two semicircular arcs and two tangential lines.
5. A hydrodynamic retarder driven runner blade as claimed in claim 4, wherein when the outside diameter of the hydraulic retarder circle is 380mm, the radius P9 of the two semicircular arcs is 3-6 mm, the radius P10 of the two tangential line segments is 10-15 mm, and the included angle P12 between the end surface of the removed part of the back surface of the blade and the edge of the blade is 15-20 °.
6. A method for designing a hydrodynamic retarder with oil flow runner blades according to any of claims 1 to 5, characterised in that it comprises the following steps:
(1) selecting a leaf shape;
selecting a common blade, wherein the common blade is provided with a front rake and a straight blade profile which is modified at the edge of the blade; the forward inclination angle is 0-45 degrees, and the thickness of the blade is 5-8 mm;
(2) determining the orientation of a design bulge structure on a blade with an oil flow passage;
setting the forward inclination angle of the common blade as the forward inclination angle of the blade with the oil flow passage, thereby determining the orientation of the bulge structure of the blade with the oil flow passage;
(3) designing the bulge structure shape of the blade with the oil passage;
the cross section of the blade bulge structure with the oil flow passage is respectively designed into a runway shape formed by two sections of large arcs and two sections of small arcs in a tangent mode; the center plane of the convex bulge structure on the blade has an offset distance with the plane of the common blade; the connecting line of the centers of the two arcs of the base structure at the top end of the blade with the oil passage and the connecting line of the centers of the two arcs of the base structure at the bottom end of the blade are in the same plane and parallel to the common blade;
(4) an oil passing flow passage oil hole is designed on the blade bulge structure;
the blade bulge structure is provided with an oil passing flow passage oil hole, and the cross section of the oil passing flow passage oil hole is in a track shape formed by two sections of semi-circular arcs and two tangent line sections; the included angle between the oil passage axis and the blade edge line on the central plane of the oil passage oil hole is marked as P11;
(5) the oil passing flow channel bulge structure correspondingly cuts the back of the blade at the edge of the blade on the front side of the impeller, the front part of the blade is reserved to form a guard plate structure, and the junction of the base body structure of the bulge structure and the common blade structure where the bulge structure is located is modified by a fillet so as to enable the bulge structure to be in smooth transition; the included angle between the end face of the removed part of the back surface of the blade and the edge of the blade is marked as P12, and the value is 15-20 degrees;
(6) the blades with the oil passing flow passages are distributed at intervals with the common blades.
7. The design method as claimed in claim 6, wherein when the external diameter of the circulation circle of the hydraulic retarder is 380mm, the radius P9 of the two semicircular arcs is 3-6 mm, and the two tangential line sections P10 are 10-15 mm.
8. The design method according to claim 6, characterized in that in the step (4), an included angle P11 between the oil passage axis on the oil passage oil hole central plane and the blade edge line is determined as follows: the oil passing flow passage is communicated with the front cavity of the impeller and the back oil suction chamber of the impeller, one end opening of the oil passing flow passage is designed at the front end of the impeller and is positioned in the middle of the cavity, and the other end opening of the oil passing flow passage is designed at the back end of the impeller and is positioned at the outer ring part of the oil suction chamber, so that the oil passage angle parameter P11 is determined.
9. The design method of claim 6, wherein in the step (4), the radius P3 of the two large arcs of the top base structure is in the range of 80-120 mm, the radius P2 of the two small arcs is in the range of 3-6 mm, the radius P6 of the two large arcs of the bottom base structure is in the range of 150-250 mm, and the radius P5 of the two small arcs is in the range of 5-8 mm.
10. The design method as claimed in claim 6, wherein in the step (4), the offset distance P8 between the central plane of the convex bulge structure on the blade and the plane of the common blade is in the range of 2-6 mm.
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| CN106090177A (en) * | 2016-07-26 | 2016-11-09 | 宁波华盛汽车部件有限公司 | A kind of stator pumps resistance wheel for Retarder in parallel |
| CN111255829A (en) * | 2018-11-30 | 2020-06-09 | 中车大连机车研究所有限公司 | Hydraulic brake stator and hydraulic brake |
-
2020
- 2020-12-17 CN CN202011516024.4A patent/CN112664590B/en active Active
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| Publication number | Priority date | Publication date | Assignee | Title |
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| EP0723089A2 (en) * | 1995-01-20 | 1996-07-24 | Voith Turbo GmbH | Hydrodynamic retarder |
| CN101903675A (en) * | 2007-12-17 | 2010-12-01 | 沃依特专利有限责任公司 | Hydrodynamic machine, in particular hydrodynamic retarder |
| CN102943832A (en) * | 2012-11-22 | 2013-02-27 | 重庆津德福科技开发有限公司 | Hydrodynamic retarder rotating impeller |
| CN203570881U (en) * | 2013-12-13 | 2014-04-30 | 宁波华盛汽车部件有限公司 | Hydraulic retarder |
| CN205503814U (en) * | 2014-07-14 | 2016-08-24 | Zf腓德烈斯哈芬股份公司 | Hydrodynamic retarder |
| CN106090177A (en) * | 2016-07-26 | 2016-11-09 | 宁波华盛汽车部件有限公司 | A kind of stator pumps resistance wheel for Retarder in parallel |
| CN111255829A (en) * | 2018-11-30 | 2020-06-09 | 中车大连机车研究所有限公司 | Hydraulic brake stator and hydraulic brake |
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| CN112664590B (en) | 2022-04-05 |
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