CN105003570B - Vortex recoil hydraulic retarder - Google Patents

Abstract

A kind of vortex backpulsing Retarder, is made up of rotor, stator and housing, rotor is made up of power transmission shaft and impeller, and impeller is provided with spoke disk, the first rotor blade and the second rotor blade；The first rotor blade and the second rotor blade are all evenly arranged around power transmission shaft, and its one is located at spoke disk card side, and another one is located at spoke disk card opposite side；Second rotor blade is symmetrical with the first rotor blade；The first rotor blade is formed by the bending plate that expansion shape is " L " shape, and " L " upper right quarter has an opening breach；Stator is made up of the first stator vane and the second stator vane, second stator vane of the first stator vane is all evenly arranged around housing cavity circumference, its one is fixed on the opening gap position of the first rotor blade, and another one is fixed on the opening gap position of the second rotor blade；Curved concave direction in a circumferential direction is contrary with stator vane for rotor blade.The present invention greatly improves retarder brake performance and effect.

Description

Vortex recoil hydraulic retarder

technical field

The invention belongs to a slow-speed braking system for a vehicle, and in particular relates to a hydraulic brake system for a vehicle, which uses fluid as the working medium and comprehensively utilizes the friction energy consumption effect when the fluid is in a high-speed vortex flow and the energy consumption effect when the fluid momentum changes. Slow braking system.

Background technique

Road transport is an important mode of transportation. With the development of my country's economy, the increasing demand for passenger and cargo transportation, the growth of the total road mileage and the continuous improvement of road surface grades, the average driving speed of road vehicles has continued to increase, and the number of serious traffic accidents has also increased, making road traffic safety problems more attention. The vehicle needs to brake to slow down during driving and turning, and it needs to brake and slow down when encountering a long-distance downhill to ensure driving safety. At present, the vast majority of road passenger and freight vehicles in China mainly use mechanical braking systems. The mechanical braking system reduces the speed of the vehicle by consuming the kinetic energy of the vehicle in the form of frictional resistance. Therefore, when the vehicle brakes and decelerates on a high-speed, curved road or a long-distance downhill road, it is often necessary for the braking system to frequently or Working for a long time will easily cause the wear and tear of the friction brake pair of the mechanical brake system, especially in high-intensity and long-term braking, it is very easy to cause the brake to fail due to the thermal decline of the brake friction pair, resulting in traffic accidents. In addition, frequent stepping on the brake pedal will also increase the fatigue of the driver and affect the driving safety of the vehicle. It can reduce or avoid the failure of the mechanical braking system, which is conducive to improving the safety performance of the vehicle.

The existing commercial retarder products mainly include electromagnetic eddy current retarder and hydraulic retarder.

The electromagnetic eddy current retarder is called "eddy current retarder" for short. Its basic structure is similar to that of a generator, and its basic working principle is to generate braking effect by magnetoelectric effect. The stator with coil winding of the eddy current retarder is fixed on the vehicle body, and the drum made of excitation material is connected with the wheel drive. When the vehicle needs to brake, a direct current is applied to the stator winding of the retarder to generate a magnetic field. When the drum rotates driven by the wheel, it cuts the magnetic force lines of the stator winding magnetic field and generates an eddy current inside the drum. When the eddy current After generation, the stator winding magnetic field will produce a force to hinder the rotation of the drum, that is, the braking force is formed on the wheel through the transmission connection between the drum and the wheel, and the magnitude of the braking force can be adjusted by controlling the current passing through the stator winding. The eddy current generated in the drum is dissipated into the air in the form of heat energy through the cooling fins on the drum. The eddy current retarder continuously converts the kinetic energy of the vehicle into the eddy current in the drum, and then converts the eddy current into heat energy, so as to consume the energy of the vehicle's motion. When the eddy current retarder works, it responds quickly and has no time lag. It can steplessly adjust the current in the coil to change the magnitude of the braking force. There are few connection relationships with other systems on the road, and the installation and maintenance are convenient, but the stator winding needs to be energized during work, which will increase the energy consumption of the vehicle.

The structure and working principle of hydraulic retarder are similar to hydraulic coupling and hydraulic torque converter. The hydraulic retarder uses oil as the working medium. It is a closed system composed of a stator with an impeller, a rotor with an impeller and a retarder housing. The housing is equipped with an inlet and outlet for working oil, and the stator is fixed. On the retarder housing, the retarder housing is fixed on the vehicle body, and the rotor is connected to the wheel in transmission. When the vehicle needs to be braked, the wheels drive the rotor impeller to rotate, and the working oil enters the retarder through the oil inlet on the retarder housing, flows at high speed under the action of the rotor impeller and impacts the stator impeller, and the rotor The energy of the impeller is transmitted to the stator impeller, but since the stator impeller is fixed on the vehicle body together with the retarder housing and cannot rotate, the rotor impeller and the stator impeller form a stirring and squeezing effect on the oil, which consumes the energy transmitted by the wheel The energy transferred to the rotor impeller makes the working oil heat up, and the kinetic energy is converted into heat energy; the heated oil flows from the oil outlet on the retarder shell through the pipeline into the double-flow separated heat exchanger for heat exchange, and the oil gets Cool and dissipate heat to the air through the cooling liquid, and the cooled oil re-enters the retarder through the oil inlet on the retarder housing. Therefore, the hydraulic retarder realizes the braking effect by converting the kinetic energy of the vehicle into the heat energy of the working oil, and the braking force can be adjusted by controlling the amount of oil entering the retarder. Compared with the electric eddy current retarder, the hydraulic retarder is widely used because of its compact structure, small size, light weight and large braking force in the low speed range. In order to avoid consuming the output power of the engine in the non-working state, the hydraulic retarder can work in two connection modes: liquid-filled start or clutch start; The interior is filled with a certain amount of working oil to form a retarding braking effect, and it takes a certain amount of time from starting to filling with a certain amount of working oil, resulting in a delay in starting; A clutch device is installed on the transmission connection path with the wheels, and the transmission connection between the retarder rotor and the wheels is interrupted when the vehicle does not need retardation braking, so as to avoid the loss of the engine output power by the retarder. In addition, because the internal structure of the retarder is similar to a hydraulic coupling or a hydraulic torque converter, the structure and processing technology are complicated, and the product manufacturing cost is relatively high.

Contents of the invention

The present invention provides a vortex recoil hydraulic retarder, the purpose of which is to give full play to the characteristics of compact structure, small volume and light weight of the hydraulic retarder, and at the same time greatly improve its retarding braking performance and effect, The manufacturing cost is reduced, and the disadvantages of starting hysteresis, low rotational speed and complex structure and processing technology are improved.

In order to achieve the above purpose, the technical solution adopted by the present invention is: a vortex recoil hydraulic retarder, which is composed of three parts: rotor, stator and housing, and its innovation lies in:

A cylindrical main flow cavity is provided in the housing, and a working fluid inlet and a working fluid outlet are arranged at intervals on the circumferential casing of the cylindrical main flow cavity, and the working fluid inlet and the working fluid outlet communicate with the main flow cavity; The communication part is provided with a partition tongue, which is a protrusion protruding inward on the circumferential inner wall of the cylindrical main flow cavity, and is used to separate the working fluid entering and exiting the main flow cavity.

The rotor is mainly composed of a transmission shaft and an impeller. The transmission shaft is located at the center of rotation of the cylindrical main flow chamber and is rotatably supported relative to the housing. One end of the transmission shaft protrudes from the housing and serves as a transmission connection end. The impeller is located at the In the cylindrical main cavity and at the center of rotation of the cylindrical main cavity, the impeller is fixedly connected to the drive shaft; the impeller is provided with a spoke disc, a set of first rotor blades and a set of second rotor blades; the spoke disc is An annular disk, the annular disk is located on the periphery of the transmission shaft and is fixedly connected to the transmission shaft. A set of first rotor blades is evenly arranged around the transmission shaft in the circumferential direction and located on one side of the disc surface, while a set of second rotor blades is evenly arranged around the drive shaft in the circumferential direction and located on the other side of the spoke disc surface ; each first rotor blade is formed by a curved thin plate with the same shape and size, wherein the planar development shape of the curved thin plate is an "L" shape, and the bottom of the "L" shape corresponds to the curved thin plate having a length Straight sides, one side of the "L" shape corresponding to the curved thin plate has a long curved side, the other side of the "L" shape corresponds to the curved thin plate has an open notch, all the long straight sides of the first rotor blade The sides are parallel to the axis of the transmission shaft and fixedly connected to the transmission shaft, and the long curved sides of all the first rotor blades are fixedly connected to the disk surface on one side of the spoke disk; the shape and size of the second rotor blade and the first rotor blade are The left-right symmetry is formed on the basis of the long curved side of the first rotor blade, the long straight sides of all the second rotor blades are parallel to the axis of the transmission shaft and fixedly connected to the transmission shaft, and the long curved sides of all the second rotor blades are connected to the other side of the spoke disc The disk surface on one side is fixedly connected; the curved concave surfaces of all the first rotor blades and all the second rotor blades in the circumferential direction of the impeller have the same orientation;

The stator is mainly composed of a group of first stator blades and a group of second stator blades, the number of a group of first stator blades is equal to that of a group of second stator blades, wherein a group of first stator blades surrounds the The cylindrical main flow cavity is evenly arranged in the circumferential direction, and is located at the open gap position of the first rotor blade, and a group of first stator blades are fixed on the inner wall of the housing on one side of the cylindrical main flow cavity; The stator blades are evenly arranged around the circumference of the cylindrical main flow cavity and are located at the open gaps of the second rotor blades, and a group of second stator blades are fixed on the inner wall of the casing on the other side of the cylindrical main flow cavity; Each first stator vane and each second stator vane are formed from a curved sheet of the same shape and size, wherein the planar unfolded shape of the curved sheet is the same as the unfolded shape of the open notch of the first rotor blade, The curved concave surfaces of all first stator blades and all second stator blades in the circumferential direction of the cylindrical main cavity are in the same orientation, while the curved concave surfaces of the first rotor blades and the first stator blades are oriented in the circumferential direction of the cylindrical main cavity on the contrary.

The relevant content in the above-mentioned technical scheme is explained as follows:

1. In the above solution, the "cylindrical main flow cavity center of rotation" refers to the rotation center of the cylindrical main flow cavity in the circumferential direction of the cylinder, and the rotation center is specifically a rotation centerline.

2. In the above solution, the "spoke disk surface" refers to the plane, end surface or side surface of the annular disk.

3. In the above solution, the "curved thin plate" refers to the structure formed after the plate is bent.

4. In the above scheme, the "planar unfolded shape of the curved thin plate is an "L" shape" means that the graphic outer contour of the blade formed by the curved thin plate in the planar unfolded state is generally L-shaped or approximately L-shaped, wherein Approximate L-shaped shapes, for example, are not right angles; the sides of the outer contour are curves instead of straight lines and other changes.

5. In the above solution, the "open gap" refers to the missing part of the upper right part of the "L"-shaped structure that is open to the outside. The shape of the open notch can be rectangular (square and rectangular), quadrilateral, pentagonal, triangular, and other geometric shapes (including curved shapes), with rectangle being the most preferred in the present invention.

6. In the above solution, in order to reduce the fluctuation range of the retarding braking force, the first rotor blade and the second rotor blade can be arranged in a misalignment in the circumferential direction of the impeller. But the present invention is not limited thereto. It is theoretically feasible to arrange the first rotor blade and the second rotor blade in equal positions in the circumferential direction of the impeller, but in actual application, the impact of the mechanical transmission parts will be caused relative to the dislocation arrangement. to increase. So the best solution is dislocation arrangement.

7. In the above scheme, in order to increase the fluidity of the working fluid in and out of the main cavity, square holes with variable cross-sections from small to large can be provided between the working fluid inlet and the working fluid outlet and the main cavity. Both the fluid inlet and the working fluid outlet are connected with the square hole with variable cross section from small to large, and communicate with the main flow chamber through the square hole with variable cross section; the partition tongue is interposed between the two square hole with variable cross section , and is located at the position where the quadrangular hole with variable cross-section communicates with the main cavity.

8. In the above solution, the number of the first rotor blades is ten to thirty-six; the number of the first stator blades is twelve to forty. These limitations on the number of rotor blades and stator blades are preferred cases, and the protection scope of the present invention is not limited thereto.

9. In the above solution, in order to facilitate the arrangement of a working fluid inlet and a working fluid outlet, a boss can be provided on the outer peripheral surface of the housing, and the working fluid inlet and a working fluid outlet are opened on the boss .

10. In the above solution, in order to better reflect the barrier effect of the partition tongue, the axial length of the partition tongue in the axial direction of the transmission shaft can be designed to be equal to the axial dimension at the outer edge of the impeller.

11. In the above solution, the rotation direction n of the rotor impeller when the impeller is working is the same as the direction of the curved concave surface of the first rotor blade and the second rotor blade in the circumferential direction of the impeller.

The working principle of the present invention is: when the present invention is applied to a vehicle, the vortex recoil type hydraulic retarder housing is fixedly connected with the vehicle body or other parts fixed on the vehicle body, and the transmission shaft and the wheel drive The working fluid inlet is connected to the working fluid supply pipeline, and the working fluid outlet is connected to the working fluid discharge pipeline. When the vehicle needs to be braked, the wheels drive the impeller to rotate through the transmission shaft, and the rotation direction of the transmission shaft (see the rotation direction n of the rotor impeller in Figure 2) is the same as the curved concave surface of the first rotor blade on the impeller in the circumferential direction of the impeller. , which is opposite to the direction of the curved concave surface of the first stator vane in the circumferential direction of the cylindrical main cavity. At this time, after the working fluid enters the main cavity of the retarder through the working fluid inlet on the retarder shell, it flows at a high speed under the action of the rotor impeller to impact the stator blades, and transfers the energy of the rotor impeller to the stator blades, but Since the stator vanes are fixed on the vehicle body together with the retarder housing and cannot rotate, the rotor impeller and the stator vanes form a stirring and squeezing effect on the working fluid. This action consumes the energy transmitted from the wheel to the rotor impeller, making the work The fluid heats up and the kinetic energy is converted into heat energy. The heated working fluid flows out from the working fluid outlet on the retarder housing through the pipeline, and the outflowing working fluid is cooled by the external fluid heat exchanger and dissipates heat to the air through the cooling liquid in the external fluid heat exchanger In the process, the cooled working fluid re-enters the retarder through the working fluid inlet on the retarder housing, thus reciprocating. The vortex recoil hydraulic retarder of the present invention realizes the braking effect by converting the kinetic energy of the vehicle into the heat energy of the working fluid, and adjusts the braking force by controlling the outlet flow and pressure of the working fluid.

Owing to adopting above-mentioned technical scheme, the beneficial technical effect of the present invention is embodied in the following aspects:

1. The vortex recoil hydraulic retarder of the present invention can accelerate the fluid entering the retarder multiple times because two sets of rotor blades (the first rotor blade and the second rotor blade) are fixed on the impeller In order to consume the energy transmitted to the impeller, the two sets of stator blades (the first stator blade and the second stator blade) fixed in the main cavity of the casing can perform multiple times on the fluid accelerated by the two sets of rotor blades passing through the impeller. Block flow and accelerate the consumption of fluid energy. The above process and characteristics enable the vortex recoil hydraulic retarder to more effectively consume the energy input through the transmission shaft when it is working, and greatly improve the retarding braking effect.

2. The vortex recoil hydraulic retarder of the present invention, since the two sets of rotor blades on the impeller have the same structural form and size, they are arranged symmetrically in the axial direction of the impeller, and the two sets of stator blades in the main cavity of the casing The structural form and size are also the same, and the axial symmetry is arranged in the main cavity, so that the impeller is easy to achieve dynamic balance during work. Working at a higher speed, the retarding braking effect is better. Under the same retarding braking effect, the external structure size is relatively small, which makes the vortex recoil hydraulic retarder lighter in weight and easy to install and connect on the vehicle. More flexible and convenient.

3. The vortex recoil hydraulic retarder of the present invention is easy to achieve dynamic balance due to the structural characteristics of the rotor. The vacuum formed by the rotation quickly sucks in the working fluid, thereby quickly forming a hydraulic retarding braking effect and shortening the starting time.

4. The vortex recoil hydraulic retarder of the present invention, when the axial seal of the transmission shaft adopts mechanical seal, can make the vortex recoil retarder not only be able to use the same oil as other existing retarder products As the working medium, the engine coolant can also be directly used as the working medium, and the engine cooling system can directly cool the working medium without using an intermediate heat exchange device such as a double-flow separation heat exchanger, so that the vortex recoil retarder can The installation and connection on the vehicle are simpler and the work is more reliable.

Description of drawings

Fig. 1 is the structural schematic diagram of the vortex recoil type hydraulic retarder of the present invention;

Fig. 2 is a partial sectional view of the vortex recoil hydraulic retarder of the present invention;

Fig. 3 is a partially enlarged view of the working fluid inlet and outlet of the vortex recoil hydraulic retarder of the present invention;

Fig. 4 is a 3D exploded view of the vortex recoil hydraulic retarder of the present invention.

Fig. 5 is a schematic diagram of the unilateral fluid flow process when the vortex recoil hydraulic retarder of the present invention is working;

Fig. 6 is a schematic diagram of the vortex generation area of the vortex recoil hydraulic retarder of the present invention.

Reference signs: 1. transmission shaft; 2. first shaft seal; 3. through-hole end cover; 4. first bearing; 5. first snap ring; 6. second bearing; 7. second shaft seal; 8 .Impeller; 9. Second snap ring; 10. Sleeve end cover; 11. Shell; 12. End cover; 13. First end cover bolt; 14. Second end cover bolt; 15. Spacer tongue; 16. 17. The first rotor blade; 18. The second rotor blade; 19. The first stator blade; 20. The second stator blade; 21. The main cavity; 22. The boss; a. Working fluid inlet; b. Working fluid outlet; h. Longitudinal height; t. Circumferential width; l. Axial length; n. Rotor impeller rotation direction; The liquid flow of the retarder; Qc. The liquid flow flowing in a unilateral annular flow inside the retarder; Qz. The liquid flow flowing between the rotor blades on one side; Qd. The liquid flow flowing between the stator blades on one side; Wz. The vortex zone between rotor blades; Wd. The vortex zone between stator blades; Wj. The vortex zone at the junction of rotor blades and stator blades.

detailed description

Below in conjunction with accompanying drawing, the present invention will be further described by embodiment:

Example: a vortex recoil hydraulic retarder

The retarder is integrally fixed on the vehicle body, and its transmission shaft 1 is connected to the vehicle wheels. After the retarder is started, the hydraulic resistance generated by the vortex flow of the internal liquid flow forms a retarding braking effect on the wheels. . The structure and working principle of the retarder in this embodiment will be described in detail below.

As shown in Figure 1-Figure 4, the retarder is generally composed of three parts: rotor, stator and housing, which are described as follows:

1. case

A cylindrical main flow chamber 21 is arranged inside the housing, and a working fluid inlet a and a working fluid outlet b are arranged at intervals on the circumferential casing of the cylindrical main flow chamber 21, and the working fluid inlet a and the working fluid outlet b are connected with the working fluid outlet b. The main cavity 21 is in communication. A partition tongue 15 is provided at the communication point, and the partition tongue 15 is a protrusion protruding inward on the circumferential inner wall of the cylindrical main flow chamber 21 for separating the working fluid entering and exiting the main flow chamber 21 .

In this embodiment, the housing is composed of a sleeve end cover 10 , an end cover 12 , a casing 11 , a set of first end cover bolts 13 and a set of second end cover bolts 14 .

The sleeve end cover 10 is formed by consolidating a cylindrical cylinder and a disc-shaped disc coaxially. The inner hole of the cylindrical cylinder is shown in FIG. The installation hole, the second bearing installation hole, the inner shoulder and the second shaft seal installation hole are distributed sequentially. A group of bolt holes evenly distributed in the circumferential direction is arranged at the outer circle of the dish-shaped disc, and the specific number of a group of bolt holes is 18-30.

The end cover 12 is a dish-shaped disc, and a group of circumferentially evenly distributed bolt holes is provided near the outer circle of the end cover 12. The number of bolt holes on a set of bolts is equal.

The cylindrical shell 11 is a cylindrical cylinder, and a set of threaded holes are evenly distributed on the circumferential end surface of the two ends of the cylindrical shell 11, and a boss 22 is fixed on the outer circle of the cylindrical shell 11. The working fluid inlet a ( threaded hole) and a working fluid outlet b (threaded hole) opened on the boss 22. Between the working fluid inlet a and the working fluid outlet b and the main flow chamber 21, there are square holes 23 with variable cross-sections from small to large. The quadrangular hole 23 with variable cross-section passes through and communicates with the main flow chamber 21 through the quadrangular hole 23 with variable cross-section. The partition tongue 15 is located between the two quadrangular holes 23 with variable cross-section, and is located at the position where the quadrangular holes 23 with variable cross-section communicate with the main cavity 21 . The radial height of the partition tongue 15 is h (see Figure 3), the circumferential width is t (see Figure 3), and its axial length is l (see Figure 1), and the partition tongue 15 is in the axial direction of the transmission shaft 1 The axial length l on is equal to the axial dimension at the outer edge of the impeller 8 .

The number of the first set of end cover bolts 13 and the set of second end cover bolts 14 is equal to the number of a set of bolt holes provided on the disc-shaped disk of the sleeve end cover 10 .

2. rotor

As shown in Figure 1, the rotor is specifically composed of a transmission shaft 1, a first shaft seal 2, a through hole cover 3, a first bearing 4, a first snap ring 5, a second bearing 6, a second shaft seal 7, an impeller 8 and a second shaft seal. Two snap rings 9 are formed.

Referring to Fig. 1, the drive shaft 1 is a solid shaft formed from the first external spline section, the first polished rod section, the second polished rod section, the shoulder and the second external spline section, which are sequentially consolidated coaxially from right to left , wherein: the diameter of the first external spline segment is smaller than the diameter of the second external spline segment, the diameter of the first polished rod segment is smaller than the second polished rod segment, and the second polished rod segment is provided with a first snap ring groove, located on the second polished rod segment A second snap ring groove is provided on the outer circle near the outer end of the outer spline segment.

The through-hole end cover 3 is a circular ring with an external thread on the outer circle and a through-step hole in the middle, wherein the step hole with a larger diameter is the first shaft seal installation hole, and the other hole is opposite to the first shaft seal installation hole. An annular boss is provided on the end surface of the side.

Referring to FIGS. 1 and 4 , the impeller 8 is specifically composed of a splined bushing, a spoke disk 16 , a set of first rotor blades 17 and a set of second rotor blades 18 . The inner circle of the spline sleeve is provided with an inner spline, and the size of the inner spline is spline-fitted with the second outer spline section of the transmission shaft 1 . The spoke disc 16 is an annular disc with a round hole in the middle, the size of the round hole is the same as the outer circle size of the spline hub and is fixedly connected with the spline hub, and the disc surface of the spoke disc 16 is perpendicular to the axis of the transmission shaft 1 . The number of the set of first rotor blades 17 and the set of second rotor blades 18 is equal, usually ten to thirty-six. One set of first rotor blades 17 is evenly arranged in the circumferential direction around the splined sleeve, and is located on one side of the disc surface of the spoke disk 16, while a set of second rotor blades 18 is evenly arranged in the circumferential direction around the splined sleeve, and Located on the other side of the disc surface of the spoke disc 16. Each first rotor blade 17 is formed by a curved thin plate with the same shape and size, wherein the planar development shape of the curved thin plate is an “L” shape, and the bottom of the “L” shape corresponds to the length of the curved thin plate. Straight side, one side of the "L" shape has a long curved side corresponding to the curved thin plate, and the other side of the "L" shape has an open gap corresponding to the curved thin plate, and the open gap is rectangular. The long straight sides of all the first rotor blades 17 are parallel to the axis of the transmission shaft 1 and fixedly connected to the spline bushing, and the long curved sides of all the first rotor blades 17 are fixedly connected to the disc surface on one side of the spoke disc 16 . The shape and size of the second rotor blade 18 and the first rotor blade 17 are left-right symmetrical based on the long curved side of the first rotor blade 17, and the long straight sides of all the second rotor blades 18 are parallel to the transmission shaft 1 axis and are fixedly connected with respect to the spline bushing, and the long curved sides of all the second rotor blades 18 are fixedly connected with the disk surface on the other side of the spoke disk 16 . The curved concave surfaces of all the first rotor blades 17 and all the second rotor blades 18 in the circumferential direction of the impeller 8 have the same orientation.

3. stator

1, 2 and 4, the stator consists of a set of first stator blades 19 and a set of second stator blades 20, a set of first stator blades 19 and a set of second stator blades 20 The number is equal (usually twelve to forty), and a group of first stator blades 19 are evenly arranged around the circumference of the cylindrical main flow cavity 21, and are located at the open notches of the first rotor blades 17 A group of first stator vanes 19 are fixed on the inner wall of the housing on one side of the cylindrical main flow cavity 21 (specifically, on the disc-shaped disc of the sleeve end cover 10 ). A group of second stator vanes 20 are evenly arranged around the circumference of the cylindrical main flow chamber 21, and are located at the open notches of the second rotor blades 18, and a group of second stator blades 20 are fixed in the cylindrical main flow chamber 21 On the inner wall of the housing on the other side (specifically fixed on the disc-shaped disc of the end cap 12). Each of the first stator vanes 19 and each of the second stator vanes 20 are formed by curved thin sheets of the same shape and size, wherein the planar expanded shape of the curved thin sheets is the same as the expanded shape of the open notch of the first rotor blade 17 The same, all the first stator blades 19 and all the second stator blades 20 have the same curved concave surface orientation in the circumferential direction of the cylindrical main flow cavity 21, while the first rotor blades 17 and the first stator blades 19 are in the same direction in the cylindrical main flow cavity. 21. The curved concave surfaces in the circumferential direction face oppositely. The first rotor blades 17 and the second rotor blades 18 are arranged offset in the circumferential direction of the impeller 8 .

4. connection relationship

Referring to Fig. 1 and Fig. 4, in the assembled state, the impeller 8 is sleeved on the second external spline section of the transmission shaft 1 through spline fit, and one end is axially positioned by a shoulder provided on the transmission shaft 1 . The second snap ring 9 is embedded in the second snap ring groove on the second outer spline section of the transmission shaft 1 to form axial positioning for the other end of the impeller 8, so that the impeller 8 can rotate synchronously with the transmission shaft 1 but cannot Axially move relative to drive shaft 1. The second shaft seal 7 is sleeved on the second polished rod section of the transmission shaft 1 near the shoulder in an elastic interference fit, so that the transmission shaft 1 can rotate relative to the second shaft seal 7 and form a rotation between the two seal. In the aforementioned combination, one end of the first external spline section of the transmission shaft 1 is inserted into the cylindrical cylinder of the sleeve end cover 10 by the side of the disc-shaped disk of the sleeve end cover 10, and the second shaft seal 7 is used for interference. The matching method is embedded in the second shaft seal installation hole of the sleeve end cover 10 . The inner ring of the second bearing 6 is sleeved on the second polished rod section of the transmission shaft 1, the outer ring of the second bearing 6 is embedded in the second bearing installation hole of the sleeve end cover 10 and one end is connected with the sleeve end cover 10 The inner shoulder of the shaft is used for axial positioning. The first snap ring 5 is inserted into the first snap ring groove provided on the second polished rod section of the transmission shaft 1 to form an axial positioning for one end of the inner ring of the second bearing 6 . The inner ring of the first bearing 4 is sleeved on the first polished rod section of the transmission shaft 1, and one end thereof is axially positioned by the step between the first polished rod section and the second polished rod section of the transmission shaft 1. The outer ring of the first bearing 4 The ring is embedded in the first bearing installation hole of the sleeve end cover 10. The through-hole end cover 3 is sleeved on the first polished rod section of the transmission shaft 1, and its outer circle is screwed into the installation hole of the through-hole end cover through threaded connection, and one end of the first bearing 4 is aligned with the annular boss on the end surface. Axial positioning is formed. The first shaft seal 2 is sleeved on the first polished rod section of the transmission shaft 1 in an elastic interference fit, so that the transmission shaft 1 can rotate relative to the first shaft seal 2 and form a rotary seal between the two. The seal 2 is embedded in the first shaft seal installation hole of the through-hole end cover 3 in an interference fit manner. One side end surface of the cylinder shell 11 is coaxially fixedly connected with the end surface of the sleeve end cover 10 provided with the first stator blade 19 through a set of first end cover bolts 13, and the other side end surface of the cylinder shell 11 is connected with the end cover 12 The end surface on the side where the second stator blade 20 is provided is coaxially fixedly connected by a set of second end cover bolts 14 . In the assembled state, the sleeve end cover 10 forms a rotational support for the transmission shaft 1 through the first bearing 4 and the second bearing 6, so that the transmission shaft 1 and the impeller 8 arranged on the transmission shaft 1 through a spline connection are relative to the casing Can be turned freely. In the assembled state, the transmission shaft 1, the first shaft seal 2, the through-hole end cover 3, the sleeve end cover 10 and the second shaft seal 7 form a sealed cavity, and the transmission shaft 1 can be connected to the sealed cavity Turn freely.

The working principle of this embodiment is as follows:

The specific installation method of the vortex recoil hydraulic retarder of the present invention on the vehicle is: the retarder shell is fixed on the vehicle body, and the transmission shaft 1 is connected to the wheel drive; in the initial state, the interior of the retarder is The working fluid is completely drained.

As shown in Figure 5 and Figure 6, when slow braking is required for the vehicle, the transmission shaft 1 connected to the wheel drive rotates under the driving force of the reverse transmission of the wheel and drives the impeller 8 to rotate synchronously (see Figure 5); the impeller 8 rotates At the same time, the air inside the hydraulic retarder is driven to make a high-speed rotary flow around the transmission shaft 1 together with it and flows between the rotor blades and the stator blades at a high speed. When the surface (the surface of the partition tongue 15 opposite to the rotation direction of the impeller 8) is at the position, due to the blocking of the partition tongue 15, a part of the air flows out of the hydraulic retarder through the working fluid outlet b, so that the back flow surface of the partition tongue 15 (the partition tongue A certain degree of vacuum is formed near the surface in the same direction as the rotation direction of the impeller 8 on 15, and this vacuum degree is transmitted to the working fluid inlet a of the vortex retarder, and then the working fluid is continuously sucked in by the working fluid inlet a; the sucked Driven by the impeller rotor 8, the working fluid rotates together with it and quickly fills the interior of the hydraulic retarder including the space between the blades; the working fluid has four flow states at the same time after entering the hydraulic retarder (see Figure 5 , Figure 6): First, an annular flow Qc is formed between the outer edge of the impeller 8 and the shell 11 (Qc is the one-sided annular liquid flow inside the retarder, for the sake of simplicity, Qc is represented by a line with an arrow The main line of the main line, its physical meaning not only indicates the flow rate, but also indicates the flow direction, the following expressions of Qi, Qo, Qz, Qd have the same meaning, where: Qo=Qi=2Qc); the second is the flow formed between the rotor blades Qz; the third is the flow Qd formed between the stator blades; the fourth is the vortex flow area Wz formed between the rotor blades, the vortex flow area Wd formed between the stator blades and the flow between each rotor blade and The vortex flow area Wj formed between the stator blades. When the impeller 8 rotates, the fluid between the rotor blades continuously flows radially between the outer edge of the impeller 8 and the shell 11 under the action of each rotor blade to form an annular flow Qc while maintaining a relatively high pressure on Qc , under the action of this relatively high pressure and under the constraint of the inner circular surface of the shell 11, a part of Qc continuously flows to both sides along the axial direction, forms Qd and enters between the stator blades and flows along the radial direction Flow in the axial direction; Qd has a tangential velocity component when it flows out between the stator blades and the speed Vd is opposite to that of the impeller 8. The axially protruding part forms a hydraulic impact; the fluid entering each rotor blade flows to the space between the outer edge of the impeller 8 and the casing 11 at Qz to supplement the part flowing out of Qc; , flows out of the retarder through the working fluid outlet b under the barrier of the partition tongue 15. , so that the external working fluid is continuously sucked into the hydraulic retarder through the working fluid inlet a; the working fluid in the vortex flow area Wz between the rotor blades and the vortex flow area Wd between the stator blades, due to the simultaneous Constrained by multiple solid interfaces, a vortex-like high-speed flow with continuously changing flow direction will be produced; with the rotation of the impeller 8, a vortex will be formed between each rotor blade and each stator blade when each rotor blade moves at a high speed relative to each stator blade. In the swirling flow area Wj, the fluid in the area Wj will also produce a vortex-like high-speed flow with a continuously changing flow direction due to the agitation effect formed by the relative motion between the blades.

During the various forms of flow of the above-mentioned working fluid, due to the continuous changes in the flow direction and flow speed of the working fluid, a part of the power input from the transmission shaft 1 is consumed; the vortex flow area Wz between the rotor blades, each stator For the working fluid in the vortex flow area Wd between the blades and the vortex flow area Wj formed between each rotor blade and stator blade, the energy loss caused by the vortex-like high-speed flow with continuously changing flow direction increases the The power consumption input by the transmission shaft 1; while the working fluid flows out from between the stator blades and flows into the rotor blades, the hydraulic impact formed by the Qd with the velocity Vd on each rotor blade further increases the power input by the transmission shaft 1. power consumption; the above-mentioned flow process is reciprocating, and the working fluid repeatedly generates friction and collision impact with the flow-through parts of the hydraulic retarder during the internal flow process of the hydraulic retarder, and is constantly squeezed, and the fluid flow velocity The size and direction constantly change and form a strong vortex, so that the energy input by the transmission shaft 1 is quickly consumed, thereby forming an efficient retarding braking effect on the driving wheel connected to the transmission shaft 1 .

When the working fluid flows inside the vortex recoil hydraulic retarder, the mechanical energy consumed by friction, collision impact, extrusion and strong vortex action is converted into heat energy, which makes the temperature of the working fluid rise rapidly. In order for the retarder to work normally, the working fluid must be cooled; the partition tongue 15 is set so that the vortex recoil hydraulic retarder can exchange fluid with the outside, and the working fluid of the hydraulic retarder flows out through the working fluid outlet b, and passes through the external After the heat exchanger is cooled, it flows back to the liquid storage tank. At the same time, the cooled working fluid is continuously inhaled from the liquid storage tank through the working fluid inlet a to ensure the normal operation of the hydraulic retarder.

When it is necessary to stop the retarding braking effect of the vortex recoil hydraulic retarder, it is only necessary to connect the working fluid inlet a to the atmosphere, and with the rotation of the impeller 8, the working fluid inside the retarder passes through the working fluid outlet b is quickly emptied and the retarding braking capability disappears.

Above embodiment just provides a kind of typical implementation of the present invention, in fact the present invention still has other changes and extensions on this basis, now for the possible changes and extensions of the present invention are described as follows:

1. In the above embodiments, the housing is composed of the sleeve end cover 10 , the end cover 12 , the casing 11 , a set of first end cover bolts 13 and a set of second end cover bolts 14 . However, those skilled in the art know that in addition to the structural forms given in the above embodiments, the housing in the present invention also has other structural forms, such as designing the end cover 12 and the cylinder shell 11 into an integrated structure and so on.

2. In the above embodiments, the transmission shaft 1 and the impeller 8 are connected through a spline fit. However, those skilled in the art know that in addition to this connection form, other connection forms can also be provided, such as common key connection, integrated connection and so on.

3. In the above embodiments, the rotation support of the transmission shaft 1 is through the cylindrical cylinder on the sleeve end cover 10 , the first bearing 4 and the second bearing 6 to form a rotation support for the transmission shaft 1 . However, those skilled in the art can easily understand that if the second bearing 6 is designed at the position corresponding to the end cover 12, it is also feasible in theory.

4. In the above embodiments, in the assembled state, the transmission shaft 1, the first shaft seal 2, the via end cover 3, the sleeve end cover 10 and the second shaft seal 7 form a sealed cavity, and the transmission shaft 1 can be relatively The sealed cavity rotates freely. However, those skilled in the art can easily understand that such a design is theoretically not unique, and there are many possible variations.

5. In the above embodiments, between the working fluid inlet a and the working fluid outlet b and the main flow chamber 21 , square holes 23 with variable cross-sections from small to large are provided. The quadrangular hole 23 with variable cross section is designed to increase the fluidity of the working fluid in and out of the main cavity, and it is not necessary in theory, it can be missing, or it can be different.

6. In the above embodiments, in order to reduce the fluctuation of the retarding braking force, the design of the impeller 8 displaces the first rotor blade 17 and the second rotor blade 18 in the circumferential direction of the impeller 8 . But the present invention is not limited thereto. If the first rotor blade 17 and the second rotor blade 18 are arranged equipotentially in the circumferential direction of the impeller 8, it is feasible in theory, but in actual application, the impact of the mechanical transmission parts will be relatively large. Increased for misplaced arrangements. Those skilled in the art can easily understand that the dislocation arrangement is only a preferred situation.

7. In the above embodiments, the defined open gap is rectangular. However, in the present invention, the "open gap" refers to the missing part of the upper right part of the "L"-shaped structure that is open to the outside. The shape of the open notch can be rectangular (square and rectangular), quadrilateral, pentagonal, triangular, and other geometric shapes (including curved shapes), with rectangle being the most preferred in the present invention. This is easily understood by those skilled in the art, and thus cannot limit the protection scope of the present invention.

8. In the above embodiments, the number of the first rotor blades is ten to thirty-six; the number of the first stator blades is twelve to forty. These limitations on the number of rotor blades and stator blades are only preferred conditions, and the protection scope of the present invention is not limited thereto, which is easily understood by those skilled in the art.

The above-mentioned embodiments are only to illustrate the technical concept and characteristics of the present invention, and the purpose is to enable those skilled in the art to understand the content of the present invention and implement it accordingly, and not to limit the protection scope of the present invention. All equivalent changes or modifications made according to the spirit of the present invention shall fall within the protection scope of the present invention.

Claims (9)

1. A vortex recoil type hydraulic retarder is composed of rotor, stator and housing, characterized in that: A cylindrical main flow cavity (21) is provided in the housing, and a working fluid inlet (a) and a working fluid outlet (b) are arranged at intervals on the circumferential casing of the cylindrical main flow cavity (21), and the working fluid inlet (a) and the working fluid outlet (b) are in communication with the main flow chamber (21); a partition tongue (15) is provided at the communication point, and the partition tongue (15) is a cylindrical main flow chamber (21) circumferential direction The inwardly protruding bump on the inner wall is used to separate the working fluid entering and leaving the main cavity (21); The rotor is mainly composed of a transmission shaft (1) and an impeller (8). The transmission shaft (1) is located at the center of rotation of the cylindrical main cavity (21) and is rotatably supported relative to the housing. The transmission shaft (1) One end protrudes from the shell and serves as the transmission connection end. The impeller (8) is located in the cylindrical main flow chamber (21) and is at the center of rotation of the cylindrical main flow chamber (21). The impeller (8) is opposite to the transmission shaft (1) fixed connection; the impeller (8) is provided with a spoke disc (16), a set of first rotor blades (17) and a set of second rotor blades (18); the spoke disc (16) is an annular disc, the The annular disk is located on the periphery of the transmission shaft (1) and is fixedly connected to the transmission shaft (1), and the surface of the spoke disk (16) is perpendicular to the axis of the transmission shaft (1); The number of the two rotor blades (18) is equal, and one group of first rotor blades (17) is evenly arranged in the circumferential direction around the transmission shaft (1), and is located on one side of the disc (16), while a group of first rotor blades (17) The two rotor blades (18) are evenly arranged in the circumferential direction around the transmission shaft (1), and are located on the other side of the disc surface of the spoke disc (16); each first rotor blade (17) is composed of curved Thin plate is formed, wherein the planar development shape of the curved thin plate is "L", the bottom of the "L" shape corresponds to the curved thin plate with a long straight side, and one side of the "L" shape corresponds to the curved thin plate It has a long curved side, and the other side of the "L" shape has an open gap corresponding to the curved thin plate. The long straight sides of all the first rotor blades (17) are parallel to the axis of the drive shaft (1) and opposite to the drive shaft. The shaft (1) is fixedly connected, and the long curved sides of all the first rotor blades (17) are fixedly connected with the disk surface on one side of the spoke disk (16); the second rotor blades (18) and the first rotor blades (17) The shape and size are symmetrical on the basis of the long curved side of the first rotor blade (17), and the long straight sides of all the second rotor blades (18) are parallel to the axis of the transmission shaft (1) and relative to the transmission shaft (1) ) are fixedly connected, and the long curved sides of all the second rotor blades (18) are fixedly connected with the disk surface on the other side of the spoke disk (16); all the first rotor blades (17) and all the second rotor blades (18) are fixed on 8) The direction of the curved concave surface in the circumferential direction is the same; The stator is mainly composed of a set of first stator blades (19) and a set of second stator blades (20), the number of a set of first stator blades (19) and a set of second stator blades (20) equal, wherein a group of first stator blades (19) are evenly arranged around the circumference of the cylindrical main flow cavity (21), and are located at the open gap position of the first rotor blade (17), a group of first stator blades The blades (19) are fixed on the inner wall of the casing on one side of the cylindrical main flow chamber (21); a group of second stator blades (20) are evenly arranged around the circumference of the cylindrical main flow chamber (21), and are located on the first At the position of the open gap of the second rotor blade (18), a group of second stator blades (20) are fixed on the inner wall of the housing on the other side of the cylindrical main cavity (21); each first stator blade ( 19) and each of the second stator blades (20) are formed by curved sheets of the same shape and size, wherein the planar unfolded shape of the curved sheets is the same as the unfolded shape of the open notch of the first rotor blade (17) , all the first stator blades (19) and all the second stator blades (20) have the same curved concave surface orientation in the circumferential direction of the cylindrical main cavity (21), while the first rotor blades (17) and the first stator blades (17) The curved concave surfaces of the blades (19) in the circumferential direction of the cylindrical main cavity (21) face oppositely. 2. The vortex recoil hydraulic retarder according to claim 1, characterized in that: the first rotor blade (17) and the second rotor blade (18) are misaligned in the circumferential direction of the impeller (8) layout. 3. The vortex recoil hydraulic retarder according to claim 1, characterized in that: the first rotor blade (17) and the second rotor blade (18) are equal in the circumferential direction of the impeller (8). bit arrangement. 4. The vortex recoil hydraulic retarder according to claim 1, characterized in that: the open notch of the first rotor blade (17) is rectangular. 5. The vortex recoil type hydraulic retarder according to claim 1, characterized in that: between the working fluid inlet (a) and the working fluid outlet (b) and the main flow chamber (21) There are square holes (23) with variable cross-sections from small to large. The cross-section quadrangular hole (23) communicates with the main cavity (21); the partition tongue (15) is between two variable cross-section quadrangular holes (23), and is located between the variable cross-section quadrangular hole (23) and the At the position where the main cavity (21) connects. 6. The vortex recoil hydraulic retarder according to claim 1, characterized in that: the number of the first rotor blades (17) is ten to thirty-six; the number of the first stator blades (19) The number is from twelve to forty. 7. The vortex recoil type hydraulic retarder according to claim 1, characterized in that: a boss (22) is provided on the outer peripheral surface of the housing, and the one working fluid inlet (a) and A working fluid outlet (b) is opened on the boss (22). 8. The vortex recoil hydraulic retarder according to claim 1, characterized in that: the axial length (l) of the partition tongue (15) in the axial direction of the transmission shaft (1) is equal to the impeller ( 8) Axial dimension at the outer edge. 9. The vortex recoil hydraulic retarder according to claim 1, characterized in that: the rotation direction (n) of the rotor impeller when the impeller (8) is working is the same as that of the first rotor blade (17) and the second rotor blade (17). The curved concave surfaces of the two rotor blades (18) in the circumferential direction of the impeller (8) face the same direction.