CN107035844B - Sectional type turbine blade of hydraulic torque converter - Google Patents
Sectional type turbine blade of hydraulic torque converter Download PDFInfo
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- CN107035844B CN107035844B CN201710375798.1A CN201710375798A CN107035844B CN 107035844 B CN107035844 B CN 107035844B CN 201710375798 A CN201710375798 A CN 201710375798A CN 107035844 B CN107035844 B CN 107035844B
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
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Abstract
本发明涉及一种液力变矩器分段化涡轮叶片，该涡轮叶片在压力面压力值为0的位置分段，其靠近涡轮进口部分的叶片为主叶片，靠近涡轮出口的叶片为尾叶片；主叶片在靠近压力面压力值为0的位置处为过渡段，该过渡段由原压力面向吸力面平移2/5～3/5叶片厚度形成，并且在压力面压力值为0的位置处圆弧连接。本发明在涡轮叶片压力面高压力区域边缘对涡轮叶片进行了分段化处理，将液力变矩器涡轮叶片设计成两段，并且主叶片向分段处过渡的区域由原压力面向吸力面平移2/5～3/5叶片厚度形成，在压力面压力值为0的位置处圆弧连接，能够达到提升涡轮压力面压力，增加涡轮转矩，提升变矩比，继而增加变矩器效率的目的。
The invention relates to a segmented turbine blade of a hydraulic torque converter. The turbine blade is segmented at a position where the pressure surface pressure value is 0. The blade near the turbine inlet is the main blade, and the blade near the turbine outlet is the tail blade ; The main blade is a transition section at the position where the pressure value of the pressure surface is 0, and the transition section is formed by the original pressure facing the suction surface by 2/5 to 3/5 of the blade thickness, and at the position where the pressure value of the pressure surface is 0 Arc connection. In the invention, the turbine blade is segmented at the edge of the high pressure area on the pressure surface of the turbine blade, the turbine blade of the torque converter is designed into two segments, and the transition area of the main blade to the segment is from the original pressure to the suction surface It is formed by translating 2/5 to 3/5 of the blade thickness, and the arc connection is made at the position where the pressure value of the pressure surface is 0, which can increase the pressure of the turbine pressure surface, increase the turbine torque, improve the torque ratio, and then increase the efficiency of the torque converter. the goal of.
Description
Technical Field
The invention belongs to the technical field of hydraulic transmission, and particularly relates to a segmental turbine blade of a hydraulic torque converter.
Background
The hydraulic torque converter is an impeller machine which transfers power by means of fluid kinetic energy, has the advantages of load self-adaption, stepless speed change, vibration reduction and isolation, stable low-speed performance and the like, and is widely applied to industries such as military industry, petroleum machinery automobiles, engineering machinery, agricultural machinery, construction machinery and the like. The torque converter as a transmission device has a lower transmission efficiency than a mechanical transmission system such as a gear transmission system, which not only limits the application range of the torque converter, but also causes waste of resources and energy and more discharge to deteriorate the environment.
The existing turbine blade of the hydraulic torque converter has the following defects:
1. the stress area of the pressure surface of the turbine is small, and the thrust borne by the turbine is small.
2. Obvious vortex is formed at the inlet of the pressure surface of the turbine blade, the flow condition at the inlet of the turbine blade is poor, and the transmission efficiency is low.
3. The oil flow loss of the maximum curvature section of the blade is huge.
Disclosure of Invention
The invention aims to provide a segmental turbine blade of a hydraulic torque converter, which can improve the pressure of a pressure surface of a turbine, thereby increasing the torque of the turbine and improving the torque ratio, improving the efficiency of the torque converter and achieving the purposes of energy conservation and efficiency improvement.
In order to solve the technical problem, the segmental turbine blade of the hydraulic torque converter is characterized in that the turbine blade is segmented at the position where the pressure value of a pressure surface is 0, the blade close to the inlet part of the turbine blade is a main blade, and the blade close to the outlet of the turbine blade is a tail blade; the main blade is a transition section at a position close to the pressure surface with the pressure value of 0, the transition section is formed by translating 2/5-3/5 blade thicknesses from the original pressure surface to the suction surface, and the main blade is connected in an arc mode at the position where the pressure value of the pressure surface is 0.
According to the method, the turbine blades are segmented at the edge of a high-pressure area of a pressure surface of the turbine blade of the torque converter according to the flow around condition of the blades in the turbine of the torque converter, the turbine blade of the torque converter is designed into two sections, an area (namely a transition section) where a main blade is transited to the segmentation position is formed by translating 2/5-3/5 blade thicknesses from an original pressure surface to a suction surface, and the blades are connected in an arc mode at a position where the pressure value of the pressure surface is 0, so that the purposes of improving the pressure surface of the turbine, increasing the torque of the turbine, improving the torque ratio and further improving the efficiency of the torque.
In a defined space coordinate system, a rotating shaft of the hydraulic torque converter is a z-axis, the direction of a turbine pointing to a pump impeller is the positive direction of the z-axis, an xoy surface is an interface of the pump impeller and the turbine, and the expression of an outer ring bone line of the main blade in the space coordinate system is
The expression of the inner ring bone line of the main blade in a space coordinate system is
The main blade and the tail blade are arranged in a butt-top mode.
The expression of the outer ring bone line of the tail vane in a space coordinate system is
The expression of the inner ring bone line of the tail vane in a space coordinate system is
The main blades and the tail blades are arranged in a staggered mode.
The expression of the outer ring bone line of the tail vane in a space coordinate system is
The expression of the inner ring bone line of the tail vane in a space coordinate system is
The main blades and the tail blades are arranged in a lap joint mode.
The expression of the outer ring bone line of the tail vane in a space coordinate system is
The expression of the inner ring bone line of the tail vane in a space coordinate system is
Compared with the original conventional hydraulic torque converter, the hydraulic torque converter has the beneficial effects that:
1. the turbine blade of the hydraulic torque converter designed by the invention increases the stress area of the pressure surface of the turbine of the hydraulic torque converter, increases the pressure of the pressure surface of the turbine of the hydraulic torque converter in the working process, and is beneficial to improving the thrust borne by the turbine, thereby improving the torque of the turbine and improving the torque ratio of the torque converter.
2. The torque converter turbine blade designed by the invention improves the flow condition at the inlet of the torque converter turbine. The flow condition at the inlet of the original conventional hydraulic torque converter is poor, obvious backflow vortexes exist at the inlet of the pressure surface of the turbine blade, and the backflow vortexes disappear after the hydraulic torque converter adopting the double-section turbine blade. The turbine blade segmentation treatment has improved the flow state at the turbine entrance, and the fluid inflow speed of increase turbine entrance has accelerated the process that fluid got into the turbine, has reduced fluid and has come out the back from the pump impeller and get into the flow loss at the turbine stage to transmit bigger moment of torsion and power, and then improve transmission efficiency.
3. The turbine blade of the hydraulic torque converter designed by the invention can eliminate the ultrahigh vortex quantity at the near wall surface of the original conventional hydraulic torque converter, and further reduces the flow loss generated by the small-scale vortex dissipation of the near wall surface boundary layer.
4. The turbine blade of the hydraulic torque converter designed by the invention enables a high-vorticity area obtained by the hydraulic torque converter in a main flow area to be larger than that of an original conventional hydraulic torque converter, and the turbulence intensity of the hydraulic torque converter is higher, so that stronger impact on the blade is generated to improve the stress of the blade.
5. The turbine blade of the hydraulic torque converter designed by the invention has the advantages that the flow loss in the turbine of the hydraulic torque converter is smaller, and the concave section of the main blade has strong micro-scale vortex motion after segmentation treatment, so that the pressure of the wall surface is promoted to be increased, the turbine torque is further improved, and the torque conversion ratio of the torque converter is improved.
6. The turbine blade of the hydraulic torque converter designed by the invention can greatly improve the performance of the hydraulic torque converter. Including maximum efficiency, stall torque ratio, nominal torque for stall conditions, etc., are all improved.
Drawings
FIG. 1 is a schematic view of a turbine blade segmentation process location selection according to the present invention;
FIG. 2 is a three-dimensional view of a torque converter turbine two-stage blade of the present invention;
FIG. 3a is a three-dimensional view of an original conventional torque converter turbine blade;
FIG. 3b-1 is a three-dimensional view of a two-stage blade of a torque converter turbine according to embodiment 1 of the present invention; FIG. 3b-2 is an enlarged partial view of portion I of FIG. 3 b-1.
FIG. 3c-1 is a three-dimensional view of a two-stage blade of a torque converter turbine according to embodiment 2 of the present invention; FIG. 3c-2 is an enlarged partial view of portion I of FIG. 3 c-1.
FIG. 3d-1 is a three-dimensional view of a torque converter turbine two-stage blade according to embodiment 3 of the present invention; FIG. 3d-2 is an enlarged partial view of portion I of FIG. 3 d-1.
FIG. 4a is a lobe pattern of an original conventional torque converter turbine blade;
FIG. 4b is a bone line view of an original conventional torque converter turbine blade;
FIG. 4c is a lobe pattern of a torque converter turbine blade according to embodiment 1 of the present invention;
FIG. 4d is a bone line view of a torque converter turbine blade according to embodiment 1 of the present invention;
FIG. 4e is a lobe pattern of a torque converter turbine blade according to embodiment 2 of the present invention;
FIG. 4f is a bone line view of a torque converter turbine blade according to embodiment 2 of the present invention;
FIG. 4g is a lobe pattern of a torque converter turbine blade according to embodiment 3 of the present invention;
FIG. 4h is a bone line view of a torque converter turbine blade according to embodiment 3 of the present invention;
FIG. 5 is a comparison of the technical effects of the torque converter of embodiment 1 of the present invention and a conventional torque converter; wherein (a) is a comparison graph of pressure velocity streamline distribution in the turbine; (b) is a vortex quantity distribution comparison diagram in the turbine; (c) a velocity field distribution comparison map in the turbine;
FIG. 6a is a comparison curve of enthalpy change trend on the same position streamline in the turbine flow field of the torque converter according to embodiment 1 of the invention and the original conventional torque converter;
FIG. 6b is a graph comparing the turbulent kinetic energy trend in the same position streamlines in the turbine flow field for the torque converter of embodiment 1 of the present invention and an original conventional torque converter;
FIG. 6c is a graph comparing the trend of turbulent kinetic energy dissipation rate variation over the same position streamlines in the turbine flow field for a torque converter according to embodiment 1 of the present invention and an original conventional torque converter;
FIG. 7a is a torque ratio comparison plot of the torque converter of embodiment 1 of the present invention versus an original conventional torque converter;
FIG. 7b is a nominal torque versus curve for the torque converter of embodiment 1 of the present invention versus an original conventional torque converter;
FIG. 7c is an efficiency comparison curve of the torque converter described in embodiment 1 of the present invention versus an original conventional torque converter.
FIG. 8a is a torque ratio comparison plot of the torque converter of embodiment 2 of the present invention versus an original conventional torque converter;
FIG. 8b is a nominal torque versus curve for the torque converter of embodiment 2 of the present invention versus an original conventional torque converter;
FIG. 8c is an efficiency comparison curve of the torque converter of embodiment 2 of the present invention versus an original conventional torque converter;
FIG. 9a is a torque ratio comparison plot of the torque converter of embodiment 3 of the present invention versus an original conventional torque converter;
FIG. 9b is a nominal torque versus curve for the torque converter of embodiment 3 of the present invention versus an original conventional torque converter;
FIG. 9c is an efficiency comparison curve of the torque converter described in embodiment 3 of the present invention versus an original conventional torque converter.
In the figure:
1. conventional vanes, 2. main vanes, 3. trailing vanes of example 1, 4. trailing vanes of example 2,
5. the caudal blade of example 3, 11, the outer circumferential rib of the conventional blade, 12, the inner circumferential rib of the conventional blade, 21, the outer circumferential rib of the main blade,
22. the inner ring bone line of the main blade, 31, the outer ring bone line of the tail blade of the embodiment 1, 32, the inner ring bone line of the tail blade of the embodiment 1, 41, the outer ring bone line of the tail blade of the embodiment 2,
42. example 2 inner ring bone line of the tail vane, 51 outer ring bone line of the tail vane of example 3, 52 inner ring bone line of the tail vane of example 3.
Detailed Description
In order to further illustrate the technical scheme of the invention, the specific implementation mode of the invention is as follows by combining the attached drawings of the specification:
the embodiment of the invention takes the three-element hydraulic torque converter as a research object, but is not limited to the application range. Firstly, CFD numerical simulation is carried out on an original conventional hydraulic torque converter, and then according to the internal blade flow-around condition of a turbine of the torque converter, on the basis of keeping the inlet and outlet angles of the original turbine blade unchanged, segmentation treatment is carried out on the turbine blade at the position (shown as A in figure 1) where the pressure value of the pressure surface of the turbine blade is 0. And defining the blades close to the inlet part of the turbine after the segmentation treatment as main blades, and defining the blades close to the outlet of the turbine as tail blades. The inlet section of the main blade is the same as the original blade, the position close to the pressure surface and with the pressure value of 0 is a transition section, the transition section is obtained by translating 2/5-3/5 blade thicknesses from the original pressure surface to the suction surface, preferably by translating 1/2 blade thicknesses from the original pressure surface to the suction surface, and the transition section is connected by a smooth arc at the position A in the figure 1; the tail leaves are obtained by adjusting the original leaves according to the shape and distribution position of the tail leaves. However, the blade form of the main blade of the present invention is not limited thereto. Three types of blade segmentation processing were performed on the turbine blade by using the three-dimensional software NX, and the processing was performed in example 1, example 2, and example 3. The three staged processing schemes yield the same main blade as the turbine blade is being processed, with only a difference in the trailing blade morphology and distribution. The main blade and the tail blade are arranged in a top-to-top mode in the embodiment 1, the main blade and the tail blade are arranged in a staggered mode in the embodiment 2, and the main blade and the tail blade are arranged in a lap mode in the embodiment 3. However, the present invention is not limited to the three main and tail vane arrangements.
Example 1
The embodiment 1 designs the turbine blade of the torque converter with the main blade 2 and the tail blade 3 arranged in a vertex-to-vertex manner (as shown in fig. 3 b-2). According to the three-dimensional model of the turbine blade in the embodiment, the blade bone line and the leaf shape are extracted, the leaf shape and the bone line of the original blade and the blade shape and the bone line obtained by the segmentation processing in the embodiment 1 of the invention are shown in fig. 4a to 4 d. In the space coordinate system of fig. 4a to 4d, the rotating shaft of the torque converter is the z-axis, the xoy plane is the interface between the pump impeller and the turbine runner, and the direction of the turbine runner pointing to the pump impeller is the positive direction of the z-axis. Extracting the three-dimensional blade bone line coordinates, and performing data processing on data points of the blade bone line by using MATLAB to obtain an expression of the blade bone line in a space coordinate system. Wherein the expression of the original conventional torque converter turbine blade outer ring skeleton line 11 in a space coordinate system is
The expression of the original conventional torque converter turbine blade inner ring skeleton line 12 in a space coordinate system is
In the embodiment 1 of the present invention, after the segmentation process, the expression of the outer ring bone line 21 of the main blade in the space coordinate system is
The expression of the inner circumferential skeleton line 22 of the main blade in the space coordinate system is
The expression of the outer ring bone line 31 of the tail vane in the space coordinate system is
The expression of the inner ring bone line 32 of the tail vane in the space coordinate system is
The torque converter model designed in embodiment 1 of the present invention is subjected to three-dimensional CFD numerical simulation calculation, and the flow field and external characteristic prediction results obtained by CFD numerical simulation are analyzed to obtain the following conclusions:
the hydraulic torque converter designed in the embodiment 1 of the invention increases the stress area of the pressure surface of the turbine, and the internal pressure of the turbine is improved in the working process of the torque converter. In fig. 5 (a), it can be clearly seen that the pressure applied to the suction surface of the turbine blade after the segmentation process is significantly higher than that of the conventional torque converter, especially in the concave section of the main blade after the segmentation process, and the pressure value is close to the highest pressure in the cascade channel. And the stress on the front edge of the main blade is improved, which is also beneficial to improving the thrust borne by the turbine, thereby improving the torque of the turbine and improving the torque ratio of the torque converter.
The torque converter designed in embodiment 1 of the invention improves the flow condition at the inlet of the turbine. As can be seen from the streamlines in fig. 5 (b), the original conventional torque converter has a significant vortex formation at the inlet of the turbine blade pressure surface, and the vortex generates a backflow of oil at the inlet of the turbine from the streamlines and flows back to the non-cascade region until being pushed into the following cascade channel by the upstream oil. The backflow vortex disappears after the turbine blade is segmented, namely the flow condition of the original conventional hydraulic torque converter at the inlet of the turbine is poor, the turbine blade segmentation improves the flow state at the inlet of the turbine, oil can enter the turbine more conveniently, the flow loss of the oil entering the turbine after coming out of the pump impeller is reduced, so that larger torque and power can be transmitted, and the transmission efficiency is improved. As can be seen in fig. 5 (b), after the blade segmentation process, the ultrahigh vortex amount at the near-wall surface of the original conventional torque converter is eliminated, which further reduces the flow loss generated by the small-scale vortex dissipation of the near-wall surface boundary layer. In the main flow region, the area of the large vorticity region obtained by the torque converter designed in the embodiment 1 of the present invention is larger than that obtained by the original conventional torque converter, which indicates that the turbulent flow strength of the torque converter designed in the embodiment 1 of the present invention is larger in the main flow region, so as to generate stronger impact on the blades to improve the stress on the blades, and in addition, from the aspect of the flow velocity shown in (c) of fig. 5, the flow velocity of the oil at the inlet of the turbine is increased by the segmented treatment of the blades, which indicates that the segmented treatment of the blades accelerates the process of the oil entering the turbine, and improves the flow condition at the inlet of the turbine.
The hydraulic torque converter designed in the embodiment 1 of the invention has small flow loss in the turbine, and the concave section of the main blade has strong micro-scale vortex motion after segmentation treatment, so that the pressure of the wall surface is promoted to be increased, the torque of the turbine is further improved, and the torque conversion ratio of the torque converter is improved. Comparing physical quantities on streamlines at the same location near the turbine blade pressure face. The trend of the change of each physical quantity is shown in fig. 6a to 6c, and the dimensionless distance "0" represents the turbine inlet and "1" represents the turbine outlet. In viscous flow, the difference in enthalpy of transfer between two points on the same flow line represents the flow loss during the fluid flow. Fig. 6a is a plot of enthalpy change on the same streamline. As can be seen from the graph, the enthalpy value of the original conventional torque converter sharply decreases at the dimensionless distance of 0.2, and tends to be stable after reaching the dimensionless distance of 0.5. The original conventional torque converter has great oil flow loss in the maximum curvature section of the blade, but the torque converter designed in the embodiment 1 of the invention starts to gradually reduce the enthalpy value at the dimensionless distance of 0.4, which shows that the flow loss of the flow liquid is more obvious when the flow liquid enters the blade segmentation treatment. In addition, the change of the enthalpy value of the original conventional torque converter is obviously higher than that of the enthalpy value of the torque converter designed in the embodiment 1 of the invention, namely the fluid flow loss of the torque converter designed in the embodiment 1 of the invention is smaller. In addition, as can be seen from fig. 6b and 6c, the turbulent kinetic energy and the dissipation rate of the turbulent kinetic energy both fluctuate greatly and sharply at the turbine blade segmentation processing position, and the change forms of the turbulent kinetic energy and the dissipation rate are substantially similar. The hydrodynamic torque converter designed in the embodiment 1 of the present invention rapidly increases at the dimensionless distance "0.4", gradually descends after reaching the peak, and approaches to the normal level at the dimensionless distance "0.6", that is, after the hydrodynamic torque converter designed in the embodiment 1 of the present invention is segmented, the turbulent kinetic energy is rapidly increased at the concave section of the main blade, that is, there is strong vortex motion at this stage, and the turbulent dissipation rate fluctuates in the same form, which indicates that the strong vortex has a small size, and the evolution and disappearance are very fast, and when the strong turbulent vortex is formed, the pressure of the wall surface is increased.
Compared with the original conventional torque converter, the performance of the torque converter designed by the embodiment 1 of the invention is greatly improved, the maximum efficiency is improved to 87.16% from 86.2%, the stall torque ratio is improved to 2.63 from 2.454, and meanwhile, the nominal torque of the stall condition is improved by 7.7%. Specific in vitro property comparison curves are shown in fig. 7 a-7 c.
Example 2
The main blades 2 and the tail blades 4 of the turbine blade of the torque converter designed by the embodiment 2 of the invention are arranged in a staggered mode (as shown in figures 3 c-2). The blade bone line and the blade shape are extracted according to the three-dimensional model of the turbine blade established in the embodiment 2, and the blade shape and the bone line obtained by the segmentation processing in the embodiment 1 of the invention are shown in fig. 4e and 4 f. Extracting the three-dimensional blade bone line coordinates, and performing data processing on data points of the blade bone line by using MATLAB to obtain an expression of the blade bone line in a space coordinate system. The expression of the main blade bone line in the space coordinate system is consistent with that of the embodiment 1, and the expression of the tail blade outer ring bone line 41 in the space coordinate system is
The expression of the inner ring bone line 42 of the tail vane in the space coordinate system is
The hydraulic torque converter designed in the embodiment 2 of the invention improves the pressure of the pressure surface of the turbine, further improves the torque of the turbine and improves the torque ratio of the torque converter. The turbine inlet flow conditions can also be improved, reducing flow losses. Torque converter performance, especially low speed performance, can be improved. The stall torque ratio is increased from 2.454 to 2.6, the starting nominal torque is increased from 180.02Nm to 194.3Nm, and the efficiency in a low speed region is obviously improved. Specific in vitro characteristic comparison curves are shown in FIGS. 8a to 8 c.
Example 3
The main blade 2 and the tail blade 5 of the turbine blade of the torque converter designed by the embodiment 3 of the invention are arranged in a lap-lap mode (as shown in a figure 3 d-2). The blade bone line and the blade shape are extracted according to the three-dimensional model of the turbine blade established in the embodiment 3, and the blade shape and the bone line obtained by the segmentation processing in the embodiment 3 are shown in fig. 4g and 4 h. Extracting the three-dimensional blade bone line coordinates, and performing data processing on data points of the blade bone line by using MATLAB to obtain an expression of the blade bone line in a space coordinate system. The expression of the main blade bone line in the space coordinate system is consistent with that of the embodiment 1, and the expression of the tail blade outer ring bone line 51 in the space coordinate system is
The expression of the inner ring bone line 52 of the tail vane in the space coordinate system is
The hydraulic torque converter designed in embodiment 3 of the invention can also improve the pressure of the pressure surface of the turbine, so that the torque of the turbine is improved, and the torque ratio of the torque converter is improved. Meanwhile, the flow state of the turbine inlet is also improved, the flow loss is reduced, and the performance of the torque converter is improved. The stall torque ratio is increased from 2.454 to 2.54, the starting nominal torque is increased from 180.02Nm to 199.22Nm, and the efficiency in a low speed region is obviously improved. Specific in vitro characteristic comparison curves are shown in FIGS. 9a to 9 c.
According to the characteristic results of the three embodiments, the invention can effectively improve the performance of the torque converter by segmenting the turbine blade.
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 to various types of torque converters without departing from the spirit and principle of the present invention shall fall within the protection scope of the present invention.
Claims (1)
1. A torque converter segmented turbine blade characterized by: the turbine blade is segmented at the position where the pressure value of the pressure surface is 0, the blade close to the inlet part of the turbine is a main blade (2), and the blade close to the outlet of the turbine is a tail blade (3); the main blade (2) is a transition section at the position close to the pressure value of 0 of the pressure surface, the transition section is formed by translating 1/2 the thickness of the blade from the original pressure surface to the suction surface, and the transition section is connected in an arc way at the position of the pressure value of 0 of the pressure surface; the main blade (2) and the tail blade (3) are arranged in a butt-top mode; in a defined space coordinate system, a rotating shaft of the hydraulic torque converter is a z-axis, the direction of a turbine pointing to a pump impeller is the positive direction of the z-axis, an xoy surface is an interface of the pump impeller and the turbine impeller, and the expression of an outer ring skeleton line (21) of the main blade (2) in the space coordinate system is shown as
The expression of the inner ring bone line (22) of the main blade (2) in a space coordinate system is
The expression of the outer ring bone line of the tail vane (3) in a space coordinate system is
The expression of the inner ring bone line of the tail vane (3) in a space coordinate system is
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| JP2009014114A (en) * | 2007-07-05 | 2009-01-22 | Jatco Ltd | Torque converter |
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| US20050262837A1 (en) * | 2004-05-27 | 2005-12-01 | Ford Global Technologies Llc | Hydrokinetic torque converter stator blade construction |
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| CN103807403A (en) * | 2014-01-28 | 2014-05-21 | 吉林大学 | Guide wheel bionic blade of double-turbine hydraulic torque converter |
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