A kind of active flow control type guide wheel assembly for hydraulic torque converter and hydraulic torque converter

Abstract

The application relates to the technical field of hydraulic transmission, and particularly discloses a guide wheel assembly for a main-flow-control type hydraulic torque converter and the hydraulic torque converter; the hydraulic torque converter comprises a pump wheel assembly, a turbine assembly and a guide wheel assembly; the guide wheel assembly comprises a guide wheel body and a positioning mechanism of a guide wheel blade tangential jet oil path; the guide wheel body comprises a guide wheel inner ring shell, a guide wheel outer ring shell and a plurality of guide wheel blades; an arc-shaped through groove is arranged on each guide wheel blade, a first side groove opening of the arc-shaped through groove is arranged on a first side wall of the guide wheel blade and closely attached to the guide wheel outer ring shell, a second side groove opening of the arc-shaped through groove is arranged on a second side wall of the guide wheel blade and closely attached to the guide wheel inner ring shell, and an arc-shaped through groove outlet is arranged between the two side groove openings and on a suction surface of the guide wheel blade; a first oil path corresponding to each arc-shaped through groove is arranged in the guide wheel outer ring shell, a second oil path is arranged in the positioning mechanism, and the first oil path is connected with an external oil injection mechanism through the second oil path. The application is favorable for improving the cavitation suppression degree in the hydraulic torque converter and improving the performance of the hydraulic torque converter.

Description

Technical Field

[0001] This invention belongs to the field of hydraulic transmission technology, and particularly relates to an active flow control type guide wheel assembly for a hydraulic torque converter and a hydraulic torque converter. Background Technology

[0002] Hydraulic torque converters are widely used in the automotive and construction machinery industries due to their advantages of continuously variable transmission, vibration isolation and damping, and torque multiplication. A hydraulic torque converter is generally located between the engine and the transmission. The simplest hydraulic torque converter consists of a pump impeller, a turbine, and a stator. The engine drives the pump impeller of the hydraulic torque converter to rotate via a flywheel. Under the action of centrifugal force, the pump impeller throws the hydraulic transmission oil inside the pump impeller out of the pump impeller, realizing the conversion of mechanical energy into fluid kinetic energy. The hydraulic transmission oil thrown out of the pump impeller impacts the turbine, thereby driving the turbine to rotate, realizing the conversion of fluid kinetic energy into mechanical energy. The turbine is connected to the output shaft, transmitting power to the transmission. The hydraulic transmission oil inside the turbine flows back to the pump impeller through the stator, achieving a circulating flow. The flow direction of the hydraulic transmission oil changes after passing through the stator, realizing the torque multiplication purpose of the hydraulic torque converter (the speed and torque of the pump impeller and turbine are similar to the lever arms and forces at both ends of a lever, and the stator is similar to the fulcrum of the lever). The hydraulic transmission fluid circulates continuously within the hydraulic torque converter, thus achieving a continuous conversion between mechanical energy and fluid kinetic energy. As an example, the structure of a conventional hydraulic torque converter is shown in patent CN110822051B.

[0003] Hydraulic torque converters are driven by engines, which typically operate at speeds of thousands of revolutions per minute. The interior of a hydraulic torque converter experiences highly developed, high-speed turbulent flow. The high speed and high energy capacity of the hydraulic torque converter increase the risk of cavitation (as the internal flow velocity increases, low pressure forms on the blade surface; when this pressure drops below a certain threshold, cavitation occurs). Cavitation can cause turbulent vibration, deterioration of energy capacity, loss of circulating flow, and fatigue erosion of the blade surface, among other problems.

[0004] Practice shows that the area near the suction surface of the guide vane is where cavitation is most severe in a hydraulic torque converter. Therefore, the most important measure to suppress cavitation in a hydraulic torque converter is to suppress the attached cavitation near the suction surface of the guide vane (or change the pressure at that location). To achieve this, in the prior art, patent CN109185416A discloses a cavitation suppression method for hydraulic torque converters based on slotting. This method involves machining straight through slots at the head of each guide vane of the hydraulic torque converter. These straight through slots run along the spanwise direction of the guide vane (from the outer ring of the guide vane to the inner ring of the guide vane), penetrating the entire guide vane. The inlet of the straight through slot is located at the head of the guide vane, and the outlet is located on the suction surface of the guide vane. The straight through slots divert the flow of fluid passing through the guide vane, thereby reducing the flow rate through the surface of the guide vane and thus reducing the degree of cavitation. The above-mentioned suppression methods have a certain degree of cavitation suppression effect on the guide wheel. However, some defects still exist. For example, the flow velocity of the jet at the outlet of the channel can only be passively controlled. It cannot control the flow velocity of the jet at the outlet of the channel in real time and under varying operating conditions according to the needs of cavitation suppression of the guide wheel. This results in incomplete suppression of cavitation in the guide wheel. Furthermore, the high-speed jet at the outlet of the straight channel will affect the fluid flow in the mainstream region under high-speed ratio conditions, thereby causing the performance of the hydraulic torque converter to deteriorate under high-speed ratio conditions (the hydraulic torque converter has cavitation under low-speed conditions and needs channel suppression, but there is no cavitation under high-speed conditions and no need for channel suppression. However, the existing channel still has flow diversion under high-speed conditions, which will lead to the performance deterioration of the hydraulic torque converter under high-speed ratio conditions), affecting the performance and reliability of the power transmission system.

[0005] The aforementioned technical problems urgently need to be solved. Summary of the Invention

[0006] Technical problems to be solved

[0007] In view of this, the purpose of the present invention is to provide an active flow control type guide wheel assembly for a hydraulic torque converter and a hydraulic torque converter using the guide wheel assembly, which is beneficial to improving the suppression effect of cavitation in the hydraulic torque converter and improving the performance of the hydraulic torque converter.

[0008] Technical solution

[0009] To achieve the above objectives, on one hand, the present invention provides an active flow control type guide wheel assembly for a hydraulic torque converter, including a guide wheel body and a positioning mechanism for the tangential jet oil passage of the guide wheel blades; the guide wheel body includes an outer ring housing, an inner ring housing, and a plurality of guide wheel blades, wherein the first sidewall of each guide wheel blade is connected to the outer ring housing and the second sidewall is connected to the inner ring housing, and the plurality of guide wheel blades are evenly spaced and uniformly distributed in a ring shape along the outer ring housing towards the inner ring housing in the circumferential direction; each guide wheel blade has an arc-shaped through groove near the head position on its suction surface;

[0010] The first side opening of the arc-shaped through groove is located on the first side wall of the guide wheel blade and is close to the outer ring shell of the guide wheel. The second side opening of the arc-shaped through groove is located on the second side wall of the guide wheel blade and is close to the inner ring shell of the guide wheel. The arc-shaped groove outlet is located between the two side openings and is opened on the suction surface of the guide wheel blade.

[0011] The outer ring housing of the guide wheel is provided with a first oil passage that corresponds to and communicates with each arc-shaped through groove, and the positioning mechanism is provided with a second oil passage. The first oil passage is connected to an external oil injection mechanism through the second oil passage.

[0012] As a further improvement to the technical solution of the present invention, the external oil injection mechanism includes a flow control valve, which is used to adjust the oil flow rate into the second oil circuit, thereby controlling the flow rate of the jet at the outlet of the arc-shaped channel.

[0013] As a further improvement to the technical solution of the present invention, the positioning mechanism includes a positioning sleeve and a mounting base. The outer ring housing of the guide wheel and the mounting base are both fixedly sleeved on the outside of the positioning sleeve, and the oil inlet of the second oil circuit is opened on the mounting base.

[0014] As a further improvement to the technical solution of the present invention, the first oil circuit includes a plurality of inlet guide posts that are connected to the arc-shaped through grooves one by one, a plurality of radial cylindrical oil circuits I that are connected to the inlet guide posts one by one, an oil collecting ring that is connected to each radial cylindrical oil circuit I, and a plurality of radial cylindrical oil circuits II that are connected to the oil collecting ring. The radial cylindrical oil circuits II are connected to the second oil circuit.

[0015] As a further improvement to the technical solution of the present invention, the three-dimensional modeling method for the guide wheel blade with the arc-shaped through groove includes the following steps:

[0016] S1. A spiral groove is constructed by intersecting a constant velocity spiral with an angle range of [-2π,π] and a logarithmic spiral with an angle range of [-π,π].

[0017] The equation for a constant velocity spiral is:

[0018]

[0019] In equation (1), a is the distance from the starting point of the constant velocity spiral to the origin of the polar coordinates, b is the growth rate of the radius of the constant velocity spiral, which controls the spacing between adjacent curves after one rotation, r is the radius of the constant velocity spiral, θ is the angle of the constant velocity spiral, and x and y are the horizontal and vertical coordinates of the constant velocity spiral, respectively.

[0020] The equation for the logarithmic spiral is:

[0021]

[0022] In equation (2), a is the growth rate coefficient of the logarithmic spiral radius, b is the growth rate coefficient of the logarithmic spiral, r is the radius of the logarithmic spiral, θ is the angle of the logarithmic spiral, and x and y are the horizontal and vertical coordinates of the logarithmic spiral, respectively.

[0023] After calculating the helix using equations (1) and (2), the logarithmic helix is ​​translated so that the starting points of the two helixes coincide, and the two helixes form two intersection points. The two intersection points and the helixes together form the helical groove.

[0024] S2. Intersect the obtained thickness distribution curves of the blade pressure surface and the blade suction surface in the original two-dimensional guide wheel blade thickness distribution curves to obtain the thickness distribution curve of the helical groove outlet and the two-dimensional helical groove.

[0025] S3. By superimposing the thickness distribution curves of the solenoid groove and the original guide wheel blade on the outer normal of the blade rib line, we can obtain the two-dimensional guide wheel blade pressure surface curve, the two-dimensional guide wheel blade suction surface curve, and the two-dimensional solenoid groove blade curve.

[0026] S4. After obtaining the original two-dimensional blade profile curve and the two-dimensional blade profile curve of the helical groove, perform a generalized conformal transformation on them to obtain the three-dimensional blade profile curve and the three-dimensional helical groove, and then obtain the three-dimensional blade of the guide wheel with the helical groove structure.

[0027] On the other hand, the present invention also provides a hydraulic torque converter using the above-mentioned guide wheel assembly, including a pump wheel assembly, a turbine assembly and a guide wheel assembly;

[0028] The guide wheel assembly includes a guide wheel body and a positioning mechanism for the tangential jet oil passage of the guide wheel blades; the guide wheel body includes an outer ring housing, an inner ring housing, and multiple guide wheel blades, wherein the first sidewall of each guide wheel blade is connected to the outer ring housing and the second sidewall is connected to the inner ring housing, and the multiple guide wheel blades are evenly spaced and uniformly distributed in a ring along the outer ring housing towards the inner ring housing; each guide wheel blade has an arc-shaped through groove near its head on its suction surface, characterized in that:

[0029] The first side opening of the arc-shaped through groove is located on the first side wall of the guide wheel blade and is close to the outer ring shell of the guide wheel. The second side opening of the arc-shaped through groove is located on the second side wall of the guide wheel blade and is close to the inner ring shell of the guide wheel. The arc-shaped through groove outlet is located between the two side openings and is opened on the suction surface of the guide wheel blade.

[0030] The outer ring housing of the guide wheel is provided with a first oil passage that corresponds to and communicates with each arc-shaped through groove, and the positioning mechanism is provided with a second oil passage. The first oil passage is connected to an external oil injection mechanism through the second oil passage.

[0031] As a further improvement to the technical solution of the present invention, the external oil injection mechanism includes a flow control valve, which is used to adjust the flow rate of oil flowing into the second oil passage in real time according to the rotational speed of the turbine in the turbine assembly, thereby controlling the flow rate of the jet at the outlet of the arc-shaped through groove.

[0032] As a further improvement to the technical solution of the present invention, the positioning mechanism includes a positioning sleeve and a mounting seat. The outer ring housing of the guide wheel and the mounting seat are both fixedly sleeved on the outside of the positioning sleeve. The oil inlet of the second oil circuit is opened in the mounting seat. The turbine output shaft in the turbine assembly passes through the positioning sleeve and the mounting seat axially.

[0033] As a further improvement to the technical solution of the present invention, the positioning mechanism is further provided with an inflow oil path for external oil to flow into the hydraulic torque converter and an outflow oil path for oil to flow out of the hydraulic torque converter. The inflow oil path and the outflow oil path are independently set and controlled from the second oil path.

[0034] As a further improvement to the technical solution of the present invention, the three-dimensional modeling method for the guide wheel blade with the arc-shaped through groove includes the following steps:

[0035] S1. A spiral groove is constructed by intersecting a constant velocity spiral with an angle range of [-2π,π] and a logarithmic spiral with an angle range of [-π,π].

[0036] The equation for a constant velocity spiral is:

[0037]

[0038] In equation (1), a is the distance from the starting point of the constant velocity spiral to the origin of the polar coordinates, b is the growth rate of the radius of the constant velocity spiral, which controls the spacing between adjacent curves after one rotation, r is the radius of the constant velocity spiral, θ is the angle of the constant velocity spiral, and x and y are the horizontal and vertical coordinates of the constant velocity spiral, respectively.

[0039] The equation for the logarithmic spiral is:

[0040]

[0041] In equation (2), a is the growth rate coefficient of the logarithmic spiral radius, b is the growth rate coefficient of the logarithmic spiral, r is the radius of the logarithmic spiral, θ is the angle of the logarithmic spiral, and x and y are the horizontal and vertical coordinates of the logarithmic spiral, respectively.

[0042] After calculating the helix using equations (1) and (2), the logarithmic helix is ​​translated so that the starting points of the two helixes coincide, and the two helixes form two intersection points. The two intersection points and the helixes together form the helical groove.

[0043] S2. Intersect the obtained thickness distribution curves of the blade pressure surface and the blade suction surface in the original two-dimensional guide wheel blade thickness distribution curves to obtain the thickness distribution curve of the helical groove outlet and the two-dimensional helical groove.

[0044] S3. By superimposing the thickness distribution curves of the solenoid groove and the original guide wheel blade on the outer normal of the blade rib line, we can obtain the two-dimensional guide wheel blade pressure surface curve, the two-dimensional guide wheel blade suction surface curve, and the two-dimensional solenoid groove blade curve.

[0045] S4. After obtaining the original two-dimensional blade profile curve and the two-dimensional blade profile curve of the helical groove, perform a generalized conformal transformation on them to obtain the three-dimensional blade profile curve and the three-dimensional helical groove, and then obtain the guide wheel blade with the helical groove structure.

[0046] Beneficial technical effects

[0047] Compared with the prior art, the active flow control type guide wheel assembly for hydraulic torque converter provided by the present invention can have, but is not limited to, the following beneficial technical effects:

[0048] First, the arc-shaped through-slot can be used to tangentially jet-impact the attached cavitation in the flow direction, changing the pressure distribution of the blade in the flow direction of the suction surface, thereby effectively suppressing cavitation;

[0049] Second, through the first and second oil circuits, a specific oil circuit is established for the tangential jet from the outside of the hydraulic torque converter housing to the inside of the guide wheel and the outlet of the arc-shaped through groove of the blade. The oil transported from the outside to the outlet of the arc-shaped through groove is convenient for outlet flow rate control, thereby realizing active flow control.

[0050] Third, the flow control valve can adjust the inlet flow rate in real time according to the turbine speed, thereby controlling the flow rate of the tangential jet at the outlet of the arc-shaped channel. When the hydraulic torque converter is in low-speed ratio operation, cavitation dynamic suppression is achieved by varying the operation and flow rate. In high-speed ratio operation, the inlet flow rate is closed, thereby eliminating the influence of the outlet jet on the mainstream flow of the guide wheel. On the one hand, cavitation dynamic suppression can be achieved in low-speed ratio operation, and on the other hand, the hydraulic performance of the hydraulic torque converter in high-speed ratio operation can be maintained.

[0051] Fourth, the inflow of external oil at the outlet of the arc-shaped channel not only suppresses the adhesion-type cavitation near the head of the suction surface of the guide wheel blade, but also replenishes the circulation flow in the mainstream area of ​​the guide wheel channel, increasing the moment of momentum of the guide wheel blade. This helps to improve the external characteristics and cavitation resistance of the hydraulic torque converter as a whole, providing guidance for the design of modern high-performance low-cavitation hydraulic torque converters.

[0052] Fifth, the parameterized construction of the solenoid groove using logarithmic and constant velocity solenoids ensures the streamlined characteristics of the solenoid groove structure, thereby reducing flow losses.

[0053] Furthermore, the hydraulic torque converter provided by the present invention utilizes the aforementioned guide wheel assembly, and therefore also possesses the aforementioned beneficial technical effects.

[0054] Advantages of additional aspects of the invention will be set forth in part in the description which follows, and in part will be obvious from the description, or may be learned by practice of the invention. Attached Figure Description

[0055] The accompanying drawings, which form part of this invention, are used to provide a further understanding of the invention. The illustrative embodiments of the invention and their descriptions are used to explain the invention and do not constitute a limitation thereof.

[0056] Figure 1 This is a cross-sectional view of the hydraulic torque converter of the present invention;

[0057] Figure 2 for Figure 1 Enlarged view of point A in the middle;

[0058] Figure 3 This is a perspective view of the guide wheel body of the present invention;

[0059] Figure 4 To and Figure 3 The flow channel model diagram corresponding to the guide wheel body in the diagram;

[0060] Figure 5 A schematic diagram of the construction of the two-dimensional helical groove of the present invention;

[0061] Figure 6 A structural diagram of the thickness distribution of the two-dimensional helical groove in this invention;

[0062] Figure 7 A two-dimensional leaf-shaped structural diagram of the helical groove of the present invention;

[0063] Figure 8 A three-dimensional structural diagram of the helical groove blade of the present invention. Detailed Implementation

[0064] To enable those skilled in the art to better understand the technical solution of the present invention, the present invention will be further described in detail below with reference to the accompanying drawings and specific embodiments.

[0065] Example 1:

[0066] like Figures 1 to 4 As shown, this embodiment provides a guide wheel assembly for use in a hydraulic torque converter, which has the feature of active flow control, and is therefore an active flow control type guide wheel assembly for a hydraulic torque converter.

[0067] The guide wheel assembly of this embodiment includes a guide wheel body and a positioning mechanism (hereinafter referred to as the positioning mechanism) for the tangential jet oil passage of the guide wheel blades; the guide wheel body includes an outer ring housing 11, an inner ring housing 12, and a plurality of guide wheel blades 13. The first sidewall of each guide wheel blade 13 is connected to the outer ring housing 11, and the second sidewall is connected to the inner ring housing 12. The plurality of guide wheel blades 13 are evenly spaced and uniformly distributed in a ring in the circumferential direction (in the direction of the hydraulic torque converter pump wheel and turbine rotation shaft) along the outer ring housing 11 toward the inner ring housing 12; an arc-shaped through groove 14 is provided on the suction surface of each guide wheel blade 13 near the head position.

[0068] The guide wheel body is the guide wheel itself; the positioning mechanism is a mechanism used to axially position and install the guide wheel body in the hydraulic torque converter; the outer ring housing 11 of the guide wheel can be regarded as the guide wheel seat, and its interior is provided with oil passage holes for generating tangential jet oil supply for the guide wheel blades; the inner ring housing 12 of the guide wheel is coaxially arranged with the outer ring housing 11 of the guide wheel. It is worth noting that the "inner" and "outer" here are not based on orientation, but on the overall function of the guide wheel in the hydraulic torque converter, which is well known to those skilled in the art; the number of guide wheel blades 13 can be determined as needed, and the two side walls of the guide wheel blades 13 can be fixedly connected to the outer ring housing 11 and the inner ring housing 12 of the guide wheel, respectively.

[0069] The first side opening of the arc-shaped through groove 14 is located on the first side wall of the guide wheel blade 13 and is in close contact with the outer ring housing 11 of the guide wheel. The second side opening of the arc-shaped through groove 14 is located on the second side wall of the guide wheel blade 13 and is in close contact with the inner ring housing 12 of the guide wheel. The arc-shaped through groove outlet 14a is located between the two side openings and is opened on the suction surface of the guide wheel blade 13. The outer ring housing 11 of the guide wheel is provided with a first oil passage corresponding to and communicating with each arc-shaped through groove 14. The positioning mechanism is provided with a second oil passage 15. The first oil passage is connected to an external oil injection mechanism (not shown in the figure) through the second oil passage 15.

[0070] The first and second sidewalls of the guide vane 13 can be respectively located on both sides of its suction surface.

[0071] An oil inlet is set near the starting point of the spiral groove at the opening of the first side groove of the arc-shaped through groove 14 (the point where the two spirals intersect and coincide). The oil flowing out of the external oil injection mechanism enters the corresponding arc-shaped through groove 14 through the second oil passage 15, the first oil passage and the area near the starting point of the spiral groove at the opening of the first side groove, and is sprayed out from the arc-shaped through groove outlet 14a, flowing to the main flow area of ​​the hydraulic torque converter. The external oil injection mechanism may include components such as an oil reservoir, pumping elements and / or control elements, as long as oil supply can be achieved.

[0072] The arc-shaped channel 14 can be used to impact the tangential jet of the attached cavitation in the flow direction, changing the pressure distribution of the blade in the flow direction of the suction surface, thereby effectively suppressing cavitation; through the first oil passage and the second oil passage 15, a specific oil passage for the tangential jet from the outside of the hydraulic torque converter housing to the inside of the guide wheel and the outlet 14a of the arc-shaped channel of the blade is established. The oil transported from the outside to the outlet 14a of the arc-shaped channel is easy to control the flow rate, thereby realizing active flow control.

[0073] In this embodiment, the external oil injection mechanism includes a flow control valve, which is used to regulate the oil flow rate into the second oil passage 15, thereby controlling the flow velocity of the jet at the arc-shaped channel outlet 14a. The flow control valve can be fixed to the positioning mechanism; by using the flow control valve, the inlet flow rate can be adjusted in real time according to the turbine speed, thereby controlling the flow velocity of the tangential jet at the arc-shaped channel outlet 14a; for example, when the hydraulic torque converter is in a low-speed ratio operating condition, cavitation dynamic suppression is achieved by varying the flow rate under different operating conditions, while the inlet flow rate is closed under high-speed ratio operating conditions, thereby eliminating the influence of the outlet jet on the mainstream flow of the guide wheel. On the one hand, cavitation dynamic suppression can be achieved under low-speed ratio operating conditions, and on the other hand, the hydraulic performance of the hydraulic torque converter can be maintained under high-speed ratio operating conditions.

[0074] In this embodiment, the positioning mechanism includes a positioning sleeve 16 and a mounting base 17. The inner ring housing 11 and the mounting base 17 are both fixedly sleeved on the outside of the positioning sleeve 16, and the oil inlet 15a of the second oil passage 15 is opened on the mounting base 17. In specific implementations, the positioning sleeve 16 and the mounting base 17 may also have other functions. For example, the positioning sleeve 16 may be an outer sleeve of the turbine output shaft 18, and the mounting base 17 may be a positioning seat for the positioning bearing 18a of the turbine output shaft 18. In this case, the turbine output shaft 18 passes through the positioning sleeve 16 and the mounting base 17 axially. A spline may be fixed or integrated on the positioning sleeve 16 to facilitate connection with the guide wheel body.

[0075] In this embodiment, the first oil passage includes multiple inlet guide posts 19 corresponding to and connected to the arc-shaped through grooves 14, multiple radial cylindrical oil passages I20 corresponding to and connected to the inlet guide posts 19, an oil collecting ring 21 connected to each radial cylindrical oil passage I20, and multiple radial cylindrical oil passages II22 connected to the oil collecting ring 21. The radial cylindrical oil passages II22 are connected to the second oil passage 15. The number of inlet guide posts 19 and radial cylindrical oil passages I20 is the same as the number of arc-shaped through grooves 14. The outlet end of the inlet guide post 19 is connected to the first side groove opening 14b of the arc-shaped through groove 14. The number of radial cylindrical oil passages II22 can be, for example, three, which are arranged at equal intervals along the circumference of the oil collecting ring 21.

[0076] Figure 4 This is a combined model 10 of the guide wheel body's flow channel and tangential jet oil path.

[0077] Example 2:

[0078] The active flow control type guide wheel assembly for hydraulic torque converter provided in this embodiment is a further improvement on the structure shown in Embodiment 1. Therefore, the same structure and principle between the two will not be described again here.

[0079] In this embodiment, the arc-shaped through groove 14 can be a helical groove structure, whose streamlined structure can reduce flow loss.

[0080] To ensure the streamlined structure of the arc-shaped through groove 14, the three-dimensional modeling method of the guide wheel blade 13 with a helical groove structure may include the following steps S1-S4.

[0081] Step S1. As Figure 5 As shown, a spiral groove (i.e., arc-shaped through groove 14) is constructed by intersecting a constant velocity spiral (Archimedean spiral) with an angle range of [-2π,π] and a logarithmic spiral (equiangular spiral) with an angle range of [-π,π].

[0082] The equation for the constant velocity spiral is:

[0083]

[0084] In equation (1), a is the distance from the starting point of the constant velocity spiral to the origin of the polar coordinates, b is the growth rate of the radius of the constant velocity spiral, which controls the spacing between adjacent curves after one rotation, r is the radius of the constant velocity spiral, θ is the angle of the constant velocity spiral, and x and y are the horizontal and vertical coordinates of the constant velocity spiral, respectively.

[0085] The equation for the logarithmic spiral is:

[0086]

[0087] In equation (2), a is the growth rate coefficient of the logarithmic spiral radius, b is the growth rate coefficient of the logarithmic spiral, r is the radius of the logarithmic spiral, θ is the angle of the logarithmic spiral, and x and y are the horizontal and vertical coordinates of the logarithmic spiral, respectively.

[0088] After calculating the helix using equations (1) and (2), the logarithmic helix is ​​translated so that the starting points of the two helixes coincide, and the two helixes form two intersection points. The two intersection points and the helixes together form the helical groove.

[0089] Step S2. Figure 6 As shown, the thickness distribution curves of the pressure surface and suction surface of the guide wheel blades in the obtained solenoid groove and the original two-dimensional guide wheel blade thickness distribution curves are intersected to obtain the solenoid groove outlet 14a and the two-dimensional solenoid groove thickness distribution curve.

[0090] Step S3. Figure 7 As shown, by superimposing the thickness distribution of the helical groove and the original guide wheel blade on the outer normal of the blade rib line 5, we can obtain the two-dimensional guide wheel blade pressure surface curve 6, the two-dimensional guide wheel blade suction surface curve 7, and the two-dimensional helical groove blade curve 8.

[0091] Regarding the calculation of the two-dimensional blade profile of the original guide wheel, the coordinates of the two-dimensional original guide wheel blade profile curve (two-dimensional coordinates of the pressure / suction surface of the two-dimensional original guide wheel blade) can be obtained by thickening the thickness distribution of the two-dimensional original guide wheel blade along the normal direction of the guide wheel rib line:

[0092]

[0093] In equation (3), the subscripts p and s represent the pressure surface and suction surface, respectively; the subscript c represents the rib line; h represents the height of the blade thickness distribution; i represents the serial number of each point; and k represents the number of the points. i φ represents the slope of the bone line. i The angle between the outer normal of the bone line and the horizontal line is represented by L and S, which represent the horizontal and vertical coordinates of the two-dimensional leaf-shaped profile curve, respectively.

[0094] Regarding the calculation of the two-dimensional spiral groove airfoil curve, the skeletal line can be used as the dividing line. The spiral groove thickness of the upper half of the skeletal line is superimposed on the skeletal line to obtain the spiral groove curve of the suction surface part. The spiral groove thickness of the lower half of the skeletal line is superimposed on the skeletal line to obtain the spiral groove curve of the suction surface part. Combining them, a complete two-dimensional spiral groove airfoil curve can be obtained.

[0095] Coordinates of the two-dimensional leaf-shaped points of the constant velocity helix on the pressure side:

[0096]

[0097] Coordinates of the two-dimensional leaf-shaped components of the constant velocity helix on the suction side:

[0098]

[0099] Coordinates of the two-dimensional leaf-shaped points of the logarithmic spiral on the pressure side:

[0100]

[0101] Coordinates of the two-dimensional leaf-shaped points of the logarithmic spiral on the suction side:

[0102]

[0103] In equations (4) to (7), the subscripts 1 and 2 represent constant velocity spirals and logarithmic spirals, respectively.

[0104] Step S4. After obtaining the original two-dimensional blade profile curve and the two-dimensional blade profile curve of the helical groove, perform a generalized conformal transformation on them to obtain the three-dimensional blade profile curve 9 and the three-dimensional helical groove, thereby obtaining the guide wheel blade 13 with the helical groove structure, such as... Figure 8 As shown.

[0105] For a detailed introduction to generalized conformal transformation, please refer to patent CN112963515A (title: Hydraulic torque converter blade shaping method based on quasi-uniform B-spline curve), which will not be elaborated here.

[0106] Example 3:

[0107] This embodiment provides a hydraulic torque converter that uses the guide wheel assembly in Embodiment 1 or Embodiment 2 above, and therefore also has the aforementioned beneficial technical effects.

[0108] like Figure 1 As shown, the hydraulic torque converter of this embodiment includes a pump wheel assembly 1, a turbine assembly 2, and a guide wheel assembly; the existing structural parts of the pump wheel assembly 1, turbine assembly 2, and guide wheel assembly can be seen, for example, in patent CN110822051B (title: A hydraulic torque converter device with integrated vibration reduction function).

[0109] The guide wheel assembly includes a guide wheel body and a positioning mechanism; the guide wheel body includes an outer ring housing 11, an inner ring housing 12, and multiple guide wheel blades 13. The first sidewall of each guide wheel blade 13 is connected to the outer ring housing 11, and the second sidewall is connected to the inner ring housing 12. The multiple guide wheel blades 13 are evenly spaced and uniformly distributed in a ring in the circumferential direction (in the direction of the hydraulic torque converter pump wheel and turbine rotation shaft) along the outer ring housing 11 toward the inner ring housing 12. An arc-shaped through groove 14 is opened on the suction surface of each guide wheel blade 13 near the head position.

[0110] The guide wheel body is the guide wheel itself; the positioning mechanism is a mechanism used to axially position the guide wheel body in the hydraulic torque converter. For the guide wheel body, the positioning mechanism is also a mechanism for positioning the tangential jet oil passage of the guide wheel blades; the outer ring housing 11 of the guide wheel can be regarded as the guide wheel seat, and its interior is provided with oil passage holes for generating tangential jet oil supply for the guide wheel blades; the inner ring housing 12 of the guide wheel is coaxially arranged with the outer ring housing 11 of the guide wheel; the number of guide wheel blades 13 can be determined as needed, and the two side walls of the guide wheel blades 13 can be fixedly connected to the outer ring housing 11 and the inner ring housing 12 of the guide wheel, respectively.

[0111] The first side opening 14b of the arc-shaped through groove 14 is located on the first side wall of the guide wheel blade 13 and is in close contact with the outer ring housing 11 of the guide wheel. The second side opening 14c of the arc-shaped through groove 14 is located on the second side wall of the guide wheel blade 13 and is in close contact with the inner ring housing 12 of the guide wheel. The arc-shaped through groove outlet 14a is located between the two side openings and is opened on the suction surface of the guide wheel blade 13. The outer ring housing 11 of the guide wheel is provided with a first oil passage corresponding to and communicating with each arc-shaped through groove 14. The positioning mechanism is provided with a second oil passage 15. The first oil passage is connected to the external oil injection mechanism through the second oil passage 15.

[0112] An oil inlet is set near the starting point of the spiral groove at the opening of the first side groove of the arc-shaped through groove 14 (the point where the two spirals intersect and coincide). The oil flowing out of the external oil injection mechanism enters the corresponding arc-shaped through groove 14 through the second oil passage 15, the first oil passage and the area near the starting point of the spiral groove at the opening of the first side groove, and is sprayed out from the arc-shaped through groove outlet 14a, flowing to the main flow area of ​​the hydraulic torque converter. The external oil injection mechanism may include components such as an oil reservoir, pumping elements and / or control elements, as long as oil supply can be achieved.

[0113] The arc-shaped channel 14 can be used to impact the tangential jet of the attached cavitation in the flow direction, changing the pressure distribution of the blade in the flow direction of the suction surface, thereby effectively suppressing cavitation; through the first oil passage and the second oil passage 15, a specific oil passage for the tangential jet from the outside of the hydraulic torque converter housing to the inside of the guide wheel and the outlet 14a of the arc-shaped channel of the blade is established. The oil transported from the outside to the outlet 14a of the arc-shaped channel is easy to control the flow rate, thereby realizing active flow control.

[0114] In this embodiment, the external oil injection mechanism includes a flow control valve. The flow control valve is used to adjust the oil flow rate into the second oil passage 15 in real time according to the turbine rotation speed in the turbine assembly, thereby controlling the flow velocity of the jet at the arc-shaped channel outlet 14a. The flow control valve can be fixed to the positioning mechanism. By using the flow control valve, the inlet flow rate can be adjusted in real time according to the turbine rotation speed, thereby controlling the flow velocity of the tangential jet at the arc-shaped channel outlet 14a. For example, when the hydraulic torque converter is in a low-speed ratio operating condition, cavitation dynamic suppression is achieved by varying the flow rate under different operating conditions. In a high-speed ratio operating condition, the inlet flow rate is closed, thereby eliminating the influence of the outlet jet on the mainstream flow of the guide wheel. On the one hand, cavitation dynamic suppression can be achieved in a low-speed ratio operating condition, and on the other hand, the hydraulic performance of the hydraulic torque converter can be maintained in a high-speed ratio operating condition.

[0115] In this embodiment, the positioning mechanism includes a positioning sleeve 16 and a mounting base 17. The outer ring housing 11 of the guide wheel and the mounting base 17 are both fixedly sleeved on the outside of the positioning sleeve 16, and the oil inlet of the second oil passage 15 is opened on the mounting base 17. In specific implementations, the positioning sleeve 16 and the mounting base 17 may also have other functions. For example, the positioning sleeve 16 may be the outer sleeve of the turbine output shaft 18, and the mounting base 17 may be the positioning seat of the positioning bearing 18a of the turbine output shaft 18. In this case, the turbine output shaft 18 passes through the positioning sleeve 16 and the mounting base 17 axially. A spline may be fixed or integrated on the positioning sleeve 16 to facilitate connection with the guide wheel body.

[0116] In this embodiment, the first oil passage may include multiple inlet guide posts 19 corresponding to and connected to the arc-shaped through grooves 14, multiple radial cylindrical oil passages I20 corresponding to and connected to the inlet guide posts 19, an oil collecting ring 21 connected to each radial cylindrical oil passage I20, and multiple radial cylindrical oil passages II22 connected to the oil collecting ring 21. The radial cylindrical oil passages II22 are connected to the second oil passage 15. The number of inlet guide posts 19 and radial cylindrical oil passages I20 is the same as the number of arc-shaped through grooves 14. The outlet end of the inlet guide post 19 is connected to the first side groove opening 14b of the arc-shaped through groove 14. The number of radial cylindrical oil passages II22 may be, for example, three, which are arranged at equal intervals along the circumference of the oil collecting ring 21.

[0117] Figure 4 This is a combined model 10 of the guide wheel body's flow channel and tangential jet oil path.

[0118] It is worth noting that the positioning mechanism also includes an inflow oil passage 23 for external oil to flow into the hydraulic torque converter and an outflow oil passage 24 for oil to flow out of the hydraulic torque converter. The inflow oil passage and the second oil passage 15 are independently configured, and they do not interfere with each other and are controlled separately. Of course, the oil flowing into the hydraulic torque converter through the second oil passage 15 also flows out through the outflow oil passage 24.

[0119] Finally, it should be noted that this article uses specific examples to illustrate the principles and implementation methods of the present invention. The above description of the embodiments is only for the purpose of helping to understand the core ideas of the present invention. Without departing from the principles of the present invention, several improvements and modifications can be made to the present invention, and these improvements and modifications also fall within the protection scope of the present invention.

Claims

1. A guide wheel assembly for active flow control in a hydraulic torque converter, comprising a guide wheel body and a positioning mechanism for a tangential jet oil passage of guide wheel blades; the guide wheel body includes an inner ring housing, an outer ring housing, and a plurality of guide wheel blades, wherein a first sidewall of each guide wheel blade is connected to the outer ring housing and a second sidewall is connected to the inner ring housing, and the plurality of guide wheel blades are evenly spaced and uniformly distributed in a ring along the outer ring housing towards the inner ring housing; each guide wheel blade has an arc-shaped through groove near its head on its suction surface, characterized in that: The first side opening of the arc-shaped through groove is located on the first side wall of the guide wheel blade and is close to the outer ring shell of the guide wheel. The second side opening of the arc-shaped through groove is located on the second side wall of the guide wheel blade and is close to the inner ring shell of the guide wheel. The arc-shaped through groove outlet is located between the two side openings and is opened on the suction surface of the guide wheel blade. The outer ring housing of the guide wheel is provided with a first oil passage that corresponds to and communicates with each arc-shaped through groove, and the positioning mechanism is provided with a second oil passage. The first oil passage is connected to an external oil injection mechanism through the second oil passage.

2. The active flow control type guide wheel assembly for a hydraulic torque converter according to claim 1, characterized in that: The external oil injection mechanism includes a flow control valve, which is used to regulate the flow rate of oil flowing into the second oil circuit, thereby controlling the flow rate of the jet at the outlet of the arc-shaped channel.

3. The active flow control type guide wheel assembly for a hydraulic torque converter according to claim 1, characterized in that: The positioning mechanism includes a positioning sleeve and a mounting base. The outer ring housing of the guide wheel and the mounting base are both fixedly sleeved on the outside of the positioning sleeve, and the oil inlet of the second oil circuit is opened on the mounting base.

4. The active flow control type guide wheel assembly for a hydraulic torque converter according to claim 1, characterized in that: The first oil circuit includes multiple inlet guide posts that are connected to the arc-shaped through grooves one by one, multiple radial cylindrical oil circuits I that are connected to the inlet guide posts one by one, an oil collecting ring that is connected to each radial cylindrical oil circuit I, and multiple radial cylindrical oil circuits II that are connected to the oil collecting ring. The radial cylindrical oil circuits II are connected to the second oil circuit.

5. The active flow control type guide wheel assembly for a hydraulic torque converter according to claim 1, characterized in that: The three-dimensional modeling method for the guide wheel blade with the aforementioned arc-shaped through groove includes the following steps: S1. A spiral groove is constructed by intersecting a constant velocity spiral with an angle range of [-2π,π] and a logarithmic spiral with an angle range of [-π,π]. The equation for a constant velocity spiral is: In equation (1), a is the distance from the starting point of the constant velocity spiral to the origin of the polar coordinates, b is the growth rate of the radius of the constant velocity spiral, which controls the spacing between adjacent curves after one rotation, r is the radius of the constant velocity spiral, θ is the angle of the constant velocity spiral, and x and y are the horizontal and vertical coordinates of the constant velocity spiral, respectively. The equation for the logarithmic spiral is: In equation (2), a is the growth rate coefficient of the logarithmic spiral radius, b is the growth rate coefficient of the logarithmic spiral, r is the radius of the logarithmic spiral, θ is the angle of the logarithmic spiral, and x and y are the horizontal and vertical coordinates of the logarithmic spiral, respectively. After calculating the helix using equations (1) and (2), the logarithmic helix is ​​translated so that the starting points of the two helixes coincide, and the two helixes form two intersection points. The two intersection points and the helixes together form the helical groove. S2. Intersect the obtained thickness distribution curves of the blade pressure surface and the blade suction surface in the original two-dimensional guide wheel blade thickness distribution to obtain the thickness distribution curve of the helical groove outlet and the two-dimensional helical groove. S3. By superimposing the thickness distribution of the helical groove and the original guide wheel blade on the outer normal of the blade rib line, we can obtain the two-dimensional guide wheel blade pressure surface curve, the two-dimensional guide wheel blade suction surface curve, and the two-dimensional helical groove blade curve. S4. After obtaining the original two-dimensional guide wheel blade profile curve and the two-dimensional helical groove blade profile curve, the three-dimensional guide wheel blade profile curve and the three-dimensional helical groove are obtained by generalized conformal transformation, and then the guide wheel blade with the helical groove structure can be obtained.

6. A hydraulic torque converter, comprising a pump impeller assembly, a turbine assembly, and a guide wheel assembly; The guide wheel assembly includes a guide wheel body and a positioning mechanism for the tangential jet oil passage of the guide wheel blades; the guide wheel body includes an outer ring housing, an inner ring housing, and multiple guide wheel blades, wherein the first sidewall of each guide wheel blade is connected to the outer ring housing and the second sidewall is connected to the inner ring housing, and the multiple guide wheel blades are evenly spaced and uniformly distributed in a ring along the outer ring housing towards the inner ring housing; each guide wheel blade has an arc-shaped through groove near its head on its suction surface, characterized in that: The first side opening of the arc-shaped through groove is located on the first side wall of the guide wheel blade and is close to the outer ring shell of the guide wheel. The second side opening of the arc-shaped through groove is located on the second side wall of the guide wheel blade and is close to the inner ring shell of the guide wheel. The arc-shaped through groove outlet is located between the two side openings and is opened on the suction surface of the guide wheel blade. The outer ring housing of the guide wheel is provided with a first oil passage that corresponds to and communicates with each arc-shaped through groove, and the positioning mechanism is provided with a second oil passage. The first oil passage is connected to an external oil injection mechanism through the second oil passage.

7. A hydraulic torque converter according to claim 6, characterized in that: The external oil injection mechanism includes a flow control valve, which is used to adjust the flow rate of oil flowing into the second oil passage in real time according to the rotational speed of the turbine in the turbine assembly, thereby controlling the flow rate of the jet at the outlet of the arc groove.

8. A hydraulic torque converter according to claim 6, characterized in that: The positioning mechanism includes a positioning sleeve and a mounting base. The inner ring housing and the mounting base are both fixedly sleeved on the outside of the positioning sleeve. The oil inlet of the second oil circuit is opened in the mounting base. The turbine output shaft in the turbine assembly passes through the positioning sleeve and the mounting base axially.

9. A hydraulic torque converter according to claim 6, characterized in that: The positioning mechanism is further provided with an inflow oil path for external oil to flow into the hydraulic torque converter and an outflow oil path for oil to flow out of the hydraulic torque converter. The inflow oil path and the second oil path are set independently.

10. A hydraulic torque converter according to claim 6, characterized in that: The three-dimensional modeling method for the guide wheel blade with the aforementioned arc-shaped through groove includes the following steps: S1. A spiral groove is constructed by intersecting a constant velocity spiral with an angle range of [-2π,π] and a logarithmic spiral with an angle range of [-π,π]. The equation for a constant velocity spiral is: In equation (1), a is the distance from the starting point of the constant velocity spiral to the origin of the polar coordinates, b is the growth rate of the radius of the constant velocity spiral, which controls the distance between two adjacent curves after one rotation, r is the radius of the constant velocity spiral, θ is the angle of the constant velocity spiral, and x and y are the horizontal and vertical coordinates of the constant velocity spiral, respectively. The equation for the logarithmic spiral is: In equation (2), a is the growth rate coefficient of the logarithmic spiral radius, b is the growth rate coefficient of the logarithmic spiral, r is the radius of the logarithmic spiral, θ is the angle of the logarithmic spiral, and x and y are the horizontal and vertical coordinates of the logarithmic spiral, respectively. After calculating the helix using equations (1) and (2), the logarithmic helix is ​​translated so that the starting points of the two helixes coincide, and the two helixes form two intersection points. The two intersection points and the helixes together form the helical groove. S2. Intersect the obtained solenoid groove with the original two-dimensional blade thickness distribution, including the blade pressure surface thickness distribution and the blade suction surface thickness distribution, to obtain the solenoid groove outlet and the two-dimensional solenoid groove thickness distribution curve; S3. By superimposing the helical groove and the original blade thickness distribution on the outer normal of the blade rib line, a two-dimensional airfoil pressure surface curve, a two-dimensional airfoil suction surface curve, and a two-dimensional helical groove airfoil curve can be obtained. S4. After obtaining the original two-dimensional blade profile curve and the two-dimensional helical groove profile curve, the blade is subjected to a generalized conformal transformation to obtain a three-dimensional blade profile curve and a three-dimensional helical groove, which can then be used to obtain a guide wheel blade with a helical groove structure.

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