CN219198040U - Variable speed torque converter - Google Patents

Abstract

The application discloses a variable speed torque converter, comprising a pump, a turbine, a one-way bearing, a housing and a housing base; one end of the pump is provided with a valve plate connected with the shell, and a main shaft of the pump is used as an input shaft to penetrate through the valve plate and then is connected with the turbine through a one-way bearing; the casing is provided with a first chamber for accommodating the one-way bearing and a second chamber for accommodating the turbine; one end of the casing, which is away from the pump, is provided with a casing base, and the turbine is arranged on the casing base; the turbine comprises an inner impeller shaft connected with the unidirectional bearing, and an outer impeller and a planetary reducer which are arranged on the inner impeller shaft; the outer impeller comprises an outer wheel body and a hollow shaft, the planetary reducer comprises a sun gear, and the inner impeller shaft is connected with the sun gear. The initial torsion of the output shaft of the speed-changing torque converter is provided by the engine in a straight line, so that the power output of the engine is optimized, the speed and torque can be automatically changed, and the problem that the engine cannot start when the engine is not loaded with oil and is not loaded with light load when the load is heavy is solved.

Description

Variable speed torque converter

Technical Field

The application relates to the technical field of transmission devices, in particular to a variable speed torque converter.

Background

The existing automatic speed changer adopts a control switch to change the speed by changing the peripheral diameter of a driving wheel (gear), has a complex structure, various gear numbers and no torque conversion capability. That is, as the load increases, the space for expanding the engine power decreases and the larger power cannot be exerted, so that the engine power is usually used in combination with the torque converter, but the torque converter not only has the capability of continuously variable transmission, but also needs to recover the transmission of 1 to 1 by means of a clutch, and the torque conversion range is less than doubled.

The existing automatic transmission adopts a plurality of control switches to achieve the aim of speed change, so that the speed change process is not smooth, the feeling of setback can be generated, and the reasonable highest rotating speed can not be achieved according to working conditions. The CVT transmission has an ideal shift process, smooth shifting, no shock feeling, but low load capacity, a narrow shift range, and no torque capacity. The torque-free capability mentioned above refers to the fact that the engine is not able to burst maximum power when the engine is subjected to heavy load and the accelerator is stepped on.

Therefore, the existing transmission has no torque conversion capability, the engine cannot be started up when being loaded heavily, and the engine cannot be started up when being loaded lightly, so that a new technical scheme is needed to solve the problems in the prior art.

Disclosure of Invention

The application provides a variable speed torque converter for solve the derailleur among the prior art and do not have torque capacity, lead to the engine to receive the heavy load when adding not play oily, receive the problem that does not play fast when light load.

In order to achieve the above object, the present application provides the following technical solutions:

the application provides a variable speed torque converter, which comprises a pump, a turbine, a one-way bearing, a housing and a housing base; the pump comprises a shell, a main shaft, a rotor, a runner, a liquid inlet, a liquid outlet and a valve plate, wherein the rotor is arranged in the shell, the valve plate is arranged at one end of the pump, the main shaft penetrates through the rotor, two ends of the main shaft extend out of two opposite ends of the shell respectively, one end of the main shaft penetrates through the valve plate and then is connected with the turbine through the one-way bearing, and the runner is communicated with the valve plate through the liquid outlet;

a first bin and a second bin are formed in the shell, the first bin is communicated with a liquid outlet on the valve plate to form a loop oil duct, and the one-way bearing is arranged in the first bin; the open end of the second bin is provided with a housing base, the turbine is arranged on the housing base, and the first bin is communicated with the second bin to form a supply oil duct;

the turbine comprises an inner impeller shaft connected with the unidirectional bearing, an outer impeller arranged in the middle of the inner impeller shaft, and a planetary reducer arranged at one end of the inner impeller shaft, wherein the outer impeller is arranged in the second bin; the outer impeller comprises an outer wheel body and a hollow shaft, the hollow shaft is connected with the planet carrier, and axial blades are arranged in the hollow shaft.

In the technical scheme, the pressure of the pump is irrelevant to the rotating speed and is relevant to torsion, and the flow of the pump is irrelevant to torsion and is relevant to the rotating speed.

Further, the pump includes a piston pump, a plunger pump, a gear pump, or a vane pump.

Further, the pump is a swash plate type axial plunger pump, and one end of the swash plate type axial plunger pump is provided with the valve plate; the open end of the first bin on the shell is provided with a flange plate which is connected with the valve plate in an adapting way.

Further, a main shaft of the swash plate type axial plunger pump penetrates through one end of the valve plate to form a one-way bearing seat matched with the one-way bearing, and the one-way bearing seat is located in the first bin.

Further, the outer wheel body comprises an upper wheel plate and a lower wheel plate, a plurality of outer wheel plates are arranged at intervals along the circumferential edge of the outer wheel body, two ends of each outer wheel plate are respectively connected with the upper wheel plate and the lower wheel plate, the upper wheel plate, the lower wheel plate and the outer wheel plates are connected to form a fluid cavity, and an inner impeller is arranged in the fluid cavity.

Further, the inner impeller comprises an inner wheel body and an inner impeller shaft, and the inner impeller shaft is coaxially arranged with the hollow shaft; the inner wheel body comprises an inner wheel plate, a plurality of inner wheel plates are arranged at intervals along the circumferential direction of the inner wheel plate, the lower wheel plate is provided with a discharge port, and the discharge port is positioned below the inner wheel body.

Further, the outer impeller is provided with an annular nozzle, the annular nozzle is located between the outer wheel piece and the inner wheel piece, the annular nozzle comprises a fluid inlet and a fluid outlet, the fluid inlet faces the outer wheel piece, and the fluid outlet faces the inner wheel piece.

Further, a planetary through hole is formed in the middle of the inner gear ring, the planet carrier and at least two planet gears are installed in the planetary through hole, the planet gears are installed in a meshed mode with the inner gear ring, and one end of the inner gear ring is fixedly connected with the housing base.

Further, one end of the inner wheel piece, which faces the outer wheel piece, is an outer end, one end of the inner wheel piece, which faces the inner impeller shaft, is an inner end, and the interval between the outer ends of two adjacent inner wheel pieces is larger than the interval between the inner ends.

Further, the annular nozzle is disposed around the outer circumference of the inner wheel body, and the fluid inlet is larger than the fluid outlet.

Further, the longitudinal cross-sectional area of the fluid inlet is at least one time greater than the longitudinal cross-sectional area of the fluid outlet.

Further, the inner circumferential surface area of the annular nozzle is at least one time larger than the area of the discharge port.

Further, the ratio of the outer diameter of the annular nozzle to the diameter of the inner wheel body is 1.5-3.

Further, the interval distance between the outer wheel sheets is equal to the length of the outer wheel sheets along the radial direction of the outer wheel body, and the length of the outer wheel sheets along the radial direction of the outer wheel body is 5% -20% of the diameter of the outer wheel body.

Further, the cross section area of the discharge port accounts for 50% -60% of the cross section area of the inner wheel body.

Further, this shell is tubular shell structure, the one end of this shell forms first bin, the other end forms the second bin, the juncture of first bin and second bin forms the mounting hole, wear to be equipped with in the mounting hole the hollow shaft, form the installation section of thick bamboo in the hollow shaft, the hollow shaft with be provided with between the installation section of thick bamboo axial blade, axial blade includes at least three, three axial blade edges the inner wall evenly distributed of hollow shaft.

Further, the central axes of the hollow shaft and the mounting cylinder coincide, and the inner impeller shaft is connected with the one-way bearing after penetrating out of the mounting cylinder.

Further, the housing base is a plate-shaped structural member adapted to the end of the housing, a mounting table protruding towards the second bin is formed on the housing base, a bearing mounting seat of the turbine is formed on the mounting table, a channel allowing an inner impeller shaft to pass through is formed on the bearing mounting seat, and the inner impeller shaft penetrates through the bearing mounting seat and then is connected with the planetary reducer.

Further, one end of the main shaft is connected with a power output shaft of the engine, and the other end of the main shaft is connected with the inner impeller shaft.

Further, the conveying sectional areas of the loop oil passage and the supply oil passage are equal to or larger than the outlet area of the annular nozzle of the turbine.

Further, the pump volume is less than or equal to 1/3 of the engine cylinder volume.

Further, the speed ratio range of the planetary reducer of the turbine is 3.4-3.7.

Compared with the prior art, the application has the following beneficial effects:

the application provides a variable speed torque converter, which comprises a pump, a turbine, a one-way bearing, a shell and a shell base, wherein one end of the pump is provided with a valve plate which can be connected with the shell, and a main shaft of the pump is used as an input shaft to penetrate through the valve plate and then is connected with the turbine through the one-way bearing; the casing is provided with a first chamber for accommodating the one-way bearing and a second chamber for accommodating the turbine; one end of the casing, which is away from the pump, is provided with a casing base, and the turbine is arranged on the casing base; the turbine comprises an inner impeller shaft connected with the one-way bearing, an outer impeller arranged in the middle of the inner impeller shaft and a planetary reducer arranged at one end of the inner impeller shaft; the outer impeller comprises an outer impeller body and a hollow shaft, the planetary reducer comprises a sun gear, a planet carrier arranged on the periphery of the sun gear, at least two planetary gears arranged on the planet carrier, and an inner gear ring arranged on the periphery of the planet carrier and meshed with the planetary gears, and the inner impeller shaft is connected with the sun gear. The input shaft of the speed-change torque converter is a main shaft of a pump (if a plunger pump is selected, the input shaft is a plunger pump shaft), and the output shaft is a planet carrier shaft of a planetary reducer of a turbine. When the engine torque pump works, the main shaft of the engine torque pump is transmitted to the inner impeller shaft to drive the planetary reducer, at the moment, the initial torque of the output shaft is provided by the engine in a straight line, the pump and the turbine are driven simultaneously after starting, the inner impeller shaft generates lower torque due to insufficient hydraulic pressure, the lower torque is unhooked with the rotating speed of the engine in the one-way bearing, but at the moment, a part of torque is provided by the inner impeller, the hydraulic pressure and the flow provided by the plunger pump are increased along with the faster starting rotating speed, and the inner impeller is separated from the input shaft to develop towards high rotating speed under the condition of allowing the load of the output shaft. When the load of the output shaft is lower, the internal pressure is increased along with the increase of the rotating speed of the turbine, the flow is smaller, the pump mainly needs larger torque force to drive the supercharging instead of the rotating speed, and the engine shows the maximum torque force value and the minimum rotating speed value, so that the purpose of continuously variable transmission of converting high torque force into high rotating speed is realized. When the load of the output shaft is larger and larger, the rotation speed of the turbine is reduced and the internal pressure is correspondingly released, at the moment, the pump mainly needs to increase the rotation speed rather than torsion, at the moment, the engine outputs larger power (namely, the throttle) under the condition, the rotation speed of the turbine is not reduced and the torsion is multiplied, the larger the load of the turbine is, the larger the released internal pressure is, the larger the engine power expansion space is, and the purpose of torque conversion is achieved. Therefore, the speed-changing torque converter provided by the application has the characteristics of automatic speed change and torque conversion, and is very flexible to use; the speed-changing torque converter provided by the application utilizes the characteristics of automatic speed change and torque change, greatly optimizes the high efficiency of the power output of the engine, and solves the problem that the engine cannot lift when the engine is not loaded with oil and is not loaded with light load when the load is heavy.

Drawings

In order to more clearly illustrate the technical solutions of the embodiments of the present application, the drawings that are needed in the embodiments will be briefly described below, and it is obvious that the drawings in the following description are only some embodiments of the present application, and that other drawings may be obtained according to these drawings without inventive effort for a person skilled in the art. It should be understood that the specific shape and configuration shown in the drawings should not be considered in general as limiting upon the practice of the present application; for example, based on the technical concepts and exemplary drawings disclosed herein, those skilled in the art have the ability to easily make conventional adjustments or further optimizations for the add/subtract/assign division, specific shapes, positional relationships, connection modes, dimensional scaling relationships, etc. of certain units (components).

FIG. 1 is a schematic diagram of the operating principle of a swash plate type axial plunger pump;

FIG. 2 is a schematic diagram of the overall structure of a torque converter according to one embodiment of the present application;

FIG. 3 is a schematic cross-sectional view of a torque converter according to one embodiment of the present disclosure;

FIG. 4 is a schematic cross-sectional view of a torque converter according to one embodiment of the present disclosure;

FIG. 5 is a schematic perspective view of a transmission torque converter according to one embodiment of the present disclosure in a semi-cut-away state;

FIG. 6 is a schematic diagram of a pump of the variable speed torque converter provided herein in one embodiment, the pump illustrated being a swash plate type axial piston pump;

FIG. 7 is a schematic perspective view of a turbine incorporating the variable speed torque converter provided herein in one embodiment;

FIG. 8 is a schematic illustration of a connection structure of a one-way bearing and an inner impeller that make up the torque converter provided herein in one embodiment;

FIG. 9 is a schematic diagram of a one-way bearing in one view that forms the torque converter of the present application in one embodiment;

FIG. 10 is a schematic illustration of a one-way bearing in another perspective that forms part of the torque converter of the present application in an embodiment;

FIG. 11 is a schematic view of the present housing that forms the torque converter of the present application in an exemplary embodiment from one perspective;

FIG. 12 is a schematic view of the present housing forming the torque converter of the present application in an alternate view in one embodiment;

FIG. 13 is a schematic view of the housing base of the present torque converter of the present application in one embodiment from one perspective;

FIG. 14 is a schematic view of the housing base of the torque converter of the present application in another perspective.

Reference numerals illustrate:

100. a pump; 110. a housing; 120. a main shaft; 130. a rotor; 140. a port plate;

200. a turbine; 210. an inner impeller; 211. an inner wheel plate; 212. an inner wheel piece; 213. an inner impeller shaft; 220. an outer impeller; 221. an outer wheel body; 222. a hollow shaft; 223. an axial vane; 230. a planetary reducer; 231. a sun gear; 232. a planet carrier; 233. a planet wheel; 234. an inner gear ring;

300. a one-way bearing;

400. the shell; 410. a first chamber; 420. a second chamber; 430. a flange plate;

500. the housing base; 510. and a bearing mounting seat.

Detailed Description

The present application is further described in detail below with reference to the attached drawings.

In the description of the present application: unless otherwise indicated, the meaning of "a plurality" is two or more. The terms "first," "second," "third," and the like in this application are intended to distinguish between the referenced objects without a special meaning in terms of technical connotation (e.g., should not be construed as emphasis on degree or order of importance, etc.). The expressions "comprising", "including", "having", etc. also mean "not limited to" (certain units, components, materials, steps, etc.).

The terms such as "upper", "lower", "left", "right", "middle", and the like, as referred to in this application, are generally used for convenience in visual understanding with reference to the drawings, and are not intended to be an absolute limitation of the positional relationship in actual products. Such changes in relative positional relationship are considered to be within the scope of the present description without departing from the technical concepts disclosed herein.

Examples

The application provides a variable speed torque converter, which consists of a pump 100, a turbine 200, a one-way bearing 300, a one-way bearing seat, a housing 400, a housing base 500 and hydraulic oil. Any pump having a characteristic that the flow rate is independent of the pressure may be used as the supply pump of the variable speed torque converter provided in the present application, such as a piston pump, a plunger pump, a gear pump, a vane pump, etc., and those skilled in the art can select the type according to the characteristics of the pump in the market when the pump is implemented.

Preferably, the turbine constituting the speed-change torque converter provided in the present application may be a turbine disclosed in chinese patent No. CN 216841826U.

In a specific application example, the swash plate type axial plunger pump can be preferably used for manufacturing the variable speed torque converter provided by the application, and the following description is made on the structural principle of the swash plate type axial plunger pump:

the swash plate type axial plunger pump mainly comprises parts such as a valve plate, a rotor, a plunger, a slipper, a pressing plate, a swash plate, a main shaft and the like. When the main shaft drives the rotor to rotate, the rotor and the plunger synchronously rotate, and the plunger makes linear reciprocating motion in the plunger hole of the rotor due to the deflection angle of the swash plate. In the oil suction area, the plunger continuously extends under the action of the central spring, the volume of the plunger cavity is continuously increased, the plunger cavity is communicated with the oil suction window of the valve plate, and oil is sucked until the upper dead point; in the oil discharging area, the plunger continuously extends into the plunger cavity under the action of the surface of the sloping cam plate, so that the volume of the plunger cavity is continuously reduced, the plunger cavity is communicated with an oil discharging window of the valve plate, and oil is discharged until the bottom dead center. When the cylinder body rotates for one circle, the plunger completes one oil suction and discharge action, and the plunger reciprocates in this way, so that oil is continuously sucked and discharged, and after a plurality of plungers uniformly distributed along the radial direction of the rotor are overlapped, continuous oil flow is formed.

Referring to fig. 1, the principle of operation of a swash plate type axial plunger pump can be summarized as follows: the pump body consists of a cylinder body 1, an eccentric wheel 2, a plunger 3, a spring 4, an oil suction valve 5, an oil discharge valve 6 and the like. The cylinder 1 is stationary, there is a good seal between the plunger 3 and the plunger bore, and it is axially movable in the plunger bore, the spring 4 always pushing the plunger against the eccentric 2. The right end (i.e. the inlet of the swash plate type axial plunger pump) of the oil suction valve 5 is communicated with the oil tank, the left end is communicated with the plunger hole in the cylinder body, and the left end (i.e. the outlet of the swash plate type axial plunger pump) is connected with the hydraulic system. When the plunger is at the bottom dead center A of the eccentric wheel, the sealing volume at the bottom of the plunger is minimum; when the eccentric wheel rotates in the direction of illustration (clockwise), the plunger continuously extends, the sealing volume is continuously enlarged, vacuum is formed, oil in the oil tank pushes away the steel ball in the oil suction valve to enter the sealing volume under the action of atmospheric pressure, the oil suction process of the pump is that the steel ball in the oil discharge valve closes the outlet under the action of the spring at the moment: when the eccentric wheel rotates to the upper dead point B, the plunger extends out of the cylinder body to the longest, the volume at the bottom of the plunger is the largest, and the oil suction process is finished. The eccentric wheel continuously rotates, the plunger is continuously compressed, the sealing volume is continuously reduced, the oil in the plunger is pressurized, the oil suction valve is closed, the oil discharge valve is opened, the oil is discharged to the outlet of the swash plate type axial plunger pump, and the oil is input into a hydraulic system; when the eccentric wheel rotates to the bottom dead center A to contact with the plunger, the sealing volume at the bottom of the plunger is minimum, and the oil discharge process is finished. The eccentric wheel rotates continuously, so that the swash plate type axial plunger pump can continuously perform oil suction and oil discharge actions, and the required flow and pressure are provided for a hydraulic system.

When the swash plate type axial plunger pump is selected for manufacturing the variable speed torque converter, the specific connection structure can be summarized as follows:

referring to fig. 3 and 4, the valve plate 140 of the swash plate type axial plunger pump is exposed outside the housing 110 and is provided as its own shaft seat, the main shaft 120 protrudes directly through the rear portion of the valve plate 140, and a sealing structure is provided at the junction of the main shaft 120 and the valve plate 140. The casing forms a sealed casing of the turbine, a second chamber 420 (namely a turbine chamber), a turbine bearing seat, a supply oil duct, a loop oil duct and a first chamber 410 (namely a unidirectional bearing seat chamber) are arranged in the sealed casing, wherein the loop oil duct and the unidirectional bearing seat share one chamber, one end of the casing is provided with a flange 430 which is in butt joint with the plunger pump, and the other end of the casing is in butt joint with the casing base 500; the one-way bearing is arranged on a one-way bearing seat provided with a step and is rigidly connected, and the one-way bearing seat is arranged on a protruding shaft of the plunger pump and is rigidly connected.

In one embodiment, the entire contents of the turbine are cited in chinese patent No. CN 216841826U. The sealed casing of the turbine disclosed in this patent is removed, a bare engine is mounted on the housing base 500, the inner impeller shaft 213 is set as a long shaft, the inner impeller 210 is mounted and fixed in the middle of the long shaft, one end of the long shaft is directly connected with the sun gear 231 of the planetary gear, the other end of the long shaft is directly connected with the inner ring of the one-way bearing and rigidly connected, the planetary reducer 230 is set as an outer impeller shaft output structure, three axial blades 223 are arranged in the hollow shaft 222 of the outer impeller 220 exhaust port for recovering the residual amount of the rotating fluid exhausted by the inner impeller 210, and all shafts of the turbine and the housing base 500 are sealed by high-precision clearance fit or rubber ring.

A first chamber 410 and a second chamber 420 are formed in the present housing 400, the first chamber 410 is communicated with a liquid outlet on the valve plate 140 to form a loop oil duct, and a one-way bearing is arranged in the first chamber 410; the second chamber 420 is provided at an open end thereof with a housing base 500, a turbine is mounted on the housing base 500, and the first chamber 410 communicates with the second chamber 420 to form a supply oil passage.

Referring to fig. 4 and 7, the turbine 200 selected in this embodiment includes an inner impeller shaft 213 connected to a one-way bearing, an outer impeller 220 installed in the middle of the inner impeller shaft 213, a planetary reducer 230 installed at one end of the inner impeller shaft 213, the outer impeller 220 being disposed in a second chamber 420, the planetary reducer 230 including a sun gear 231, a planet carrier 232 disposed at the periphery of the sun gear 231, at least two planet gears 233 installed on the planet carrier 232, and an inner gear ring 234 disposed at the periphery of the planet carrier 232 and engaged with the planet gears 233, the inner impeller shaft 213 being connected to the sun gear 231; the outer impeller 220 includes an outer wheel body 221 and a hollow shaft 222, the hollow shaft 222 is connected with a planet carrier 232, and axial blades 223 are arranged inside the hollow shaft 222.

The outer wheel body 221 comprises an upper wheel plate and a lower wheel plate, a plurality of outer wheel plates are arranged at intervals along the circumferential edge of the outer wheel body 221, two ends of each outer wheel plate are respectively connected with the upper wheel plate and the lower wheel plate, the upper wheel plate, the lower wheel plate and the outer wheel plates are connected to form a fluid cavity, and an inner impeller 210 is arranged in the fluid cavity. The inner impeller 210 includes an inner wheel body and an inner impeller shaft 213, the inner impeller shaft 213 being coaxially mounted with the hollow shaft 222; the inner wheel body comprises an inner wheel plate 211, a plurality of inner wheel plates 212 are arranged along the circumferential direction of the inner wheel plate 211 at intervals, the lower wheel plate is provided with a discharge port, and the discharge port is positioned below the inner wheel body correspondingly. The outer impeller 220 is provided with an annular nozzle located between the outer and inner wheel pieces 212, the annular nozzle comprising a fluid inlet towards the outer wheel piece and a fluid outlet towards the inner wheel piece 212.

A planetary through hole is formed in the middle of the inner gear ring 234, the planet carrier 232 and at least two planet gears 233 are arranged in the planetary through hole, the planet gears 233 are meshed with the inner gear ring 234, and one end of the inner gear ring 234 is fixedly connected with the housing base 500. The inner wheel plates 212 have an outer end facing the outer wheel plates, and the inner wheel plates 212 have an inner end facing the inner impeller shaft 213, and the interval between the outer ends of the adjacent inner wheel plates 212 is larger than the interval between the inner ends.

Referring to fig. 11 and 12, the present housing provided herein is a cylindrical housing 110 structure, one end of the present housing forms a first chamber 410, the other end forms a second chamber 420, a junction of the first chamber 410 and the second chamber 420 forms a mounting hole, a hollow shaft 222 is penetrated in the mounting hole, a mounting cylinder is formed in the hollow shaft 222, an axial blade 223 is provided between the hollow shaft 222 and the mounting cylinder, the axial blade 223 comprises at least three axial blades 223, and the three axial blades 223 are uniformly distributed along the inner wall of the hollow shaft 222. The hollow shaft 222 coincides with the central axis of the mounting cylinder, and the inner impeller shaft 213 is connected with the one-way bearing after penetrating out of the mounting cylinder.

Referring to fig. 13 and 14, the present housing frame 500 provided herein is a plate-shaped structural member adapted to an end of the present housing, a mounting table protruding toward the second chamber 420 is formed on the present housing frame 500, the mounting table forms a bearing mount 510 of the turbine, a passage allowing the inner impeller shaft 213 to pass through is formed on the bearing mount 510, and the inner impeller shaft 213 is connected to the planetary reducer 230 after passing through the bearing mount 510. One end of the main shaft 120 of the pump provided by the application is connected with the power output shaft of the engine, and the other end is connected with the inner impeller shaft 213.

In one embodiment, the speed ratio of the outer impeller 220 to the inner impeller 210 of the turbine may be set to 3.3, at which time at least three axial blades 223 may be set inside the hollow shaft 222 at the discharge port of the outer impeller 220 for recovering the high-speed rotating liquid discharged from the inner impeller 210 to reduce the loss, and the remaining amount is considerable as tested by the inventor.

The main design principle of the speed and torque converter provided by the application is based on: 1. the torque of the engine is mainly needed at high pressure instead of the rotating speed, and the rotating speed of the engine is mainly needed at low pressure instead of the rotating speed, so that a proper pump is selected, and the pump needs to have the characteristics that the pressure of the pump is independent of the rotating speed and is related to the torque, and the flow of the pump is independent of the torque and is related to the rotating speed. 2. The high torque force of the engine is converted into Gao Yeya by the pump and is provided for the turbine, the turbine converts high hydraulic pressure into high rotating speed, the pressure of the pump is mainly required to be not the flow rate at the high rotating speed, the flow rate of the pump is mainly required to be not the pressure at the low rotating speed, on the basis, the turbine which can convert the high pressure into the high rotating speed and can automatically allocate the pressure and flow utilization ratio is selected, and the turbine disclosed in the Chinese patent No. 216841826U just has the characteristics of converting the high pressure into the high rotating speed and automatically allocating the pressure and flow utilization ratio according to the working condition.

The following describes the operation principle of the speed-change torque converter provided in the present application: the input shaft of the variable speed torque converter is the main shaft 120 of the pump (the pump can be a plunger pump, the input shaft is a plunger pump shaft), and the output shaft is the planet carrier 232 shaft of the speed reducer of the turbine. When the engine is in operation, the engine twists the plunger pump shaft to drive the reducer to the inner impeller shaft 213, at the moment, the initial torsion of the output shaft is provided by the engine in a straight line, after starting, the plunger pump and the turbine are simultaneously driven, the inner impeller shaft 213 generates lower torsion due to insufficient hydraulic pressure, and is unhooked with the rotating speed of the engine in a one-way bearing, but at the moment, a part of torsion is provided by the inner impeller 210, and as the starting rotating speed is faster and faster, the hydraulic pressure and flow provided by the plunger pump are also increased, and under the condition of allowing the load of the output shaft, the inner impeller 210 is separated from the input shaft to develop towards high rotating speed. When the load of the output shaft is lower, the internal pressure is increased along with the increase of the rotating speed of the turbine, the flow is smaller, the plunger pump mainly needs larger torque force to drive the pressurization instead of the rotating speed, and the engine shows the maximum torque force value and the minimum rotating speed value, so that the purpose of continuously variable transmission of converting high torque force into high rotating speed is realized. When the load of the output shaft is larger and larger, the rotation speed of the turbine is reduced and the internal pressure is correspondingly released, at the moment, the plunger pump mainly needs to increase the rotation speed rather than the torsion force, at the moment, the engine outputs larger power (namely, the throttle) under the condition, the rotation speed of the turbine is not reduced and the torsion force is multiplied, the larger the load of the turbine is, the larger the released internal pressure is, the larger the engine power expansion space is, and the purpose of torque conversion is realized. Therefore, the speed-changing torque converter provided by the application has the characteristics of automatic speed change and torque conversion, and is very flexible in usability.

Furthermore, because the speed of the engine is extremely high at no-load and can reach 95% of the actual flow rate of the pressure, the speed is limited by the rear speed reducer, which means that the starting torque is extremely large, and the speed-changing torque converter has the characteristic of torque conversion.

The speed and torque converter provided by the application utilizes the characteristics of automatic speed change and torque change, greatly optimizes the high efficiency of the power output of the engine, solves the problem that the engine cannot start when the engine is not loaded with oil and is loaded with light load, and also solves some defects of the existing automatic gearbox. In addition, the speed and torque changing device does not need any auxiliary devices such as a control switch, is good in stability, and is in a straight line in the speed and torque changing process.

The speed and torque change device provided by the application realizes the purposes of speed change and distance change by utilizing the structural characteristics of the pump and the turbine, and the traditional speed changer realizes speed change by changing the circumference of the driving wheel, so that the working principle of the speed and torque change device and the working principle of the traditional speed changer are two different concepts.

In short, the implementation principle of the variable speed torque converter mainly depends on the increase and release of the internal pressure of the turbine to achieve the purpose, the variable speed quantity and the torque quantity are directly related to the configuration of the engine, when the output shaft is in heavy load, the internal pressure of the turbine is close to zero, and the torque quantity is increased in geometric multiple; when the output shaft load is close to zero, the turbine internal pressure is close to full pressure, and the speed change amount is tens of times longer.

If the variable speed torque converter provided by the application selects the plunger pump, the swash plate type axial plunger pump is ideal, the quantitative plunger pump or the variable plunger pump can be adopted, the quantitative plunger pump is adopted for working in the known occasion, the variable plunger pump is adopted for working in the unknown or different occasions, so that the variable speed torque converter can be multipurpose by one machine, and the superior variable speed torque capacity can be realized through the conventional hydraulic inductive switch, for example, the swash plate is aligned to the turbine to fail, and the torque is provided by the engine straight line.

The variable speed torque converter provided by the application is subjected to turbine entity test during actual machining and manufacturing. In turbine physical testing, the conversion efficiency of the turbine to the pressure head is as high as 95%, and the idle rotation speed of the turbine is almost equal to the actual flow rate of the pressure head when the engine provides effective pressure, so that the configuration of the engine and the parameters of the rear speed reducer are determined by taking the important reference into consideration.

Further, in the turbine physical test, the sum of the rotational speed of the outer impeller 220 and the flow rate of the fluid can be expanded 1.5 times to reach the inner impeller 210 (i.e., 1.5 times the circumferential speed of the inner impeller 210) through the annular nozzle of the turbine, so that the volume provided by the plunger pump is calculated by taking the minimum rotational speed of the inner impeller 210 per second as a basic unit, the outlet flow rate of the plunger pump is 1/3 of the circumferential speed of the inner impeller 210 through the annular nozzle, and the value cannot be too high because the liquid can generate extremely large centrifugal force when the turbine runs at high speed, otherwise, the ideal space for expanding the power cannot be obtained under heavy load, and the engine can bear unreasonable torque under empty load. Or by another calculation method, for example, the existing engine cylinder pressure is basically 1.5 megapascals, the volume of the plunger pump cannot exceed 1/3 of the volume of the engine cylinder, the turbine is ensured not to exceed 30% of the actual flow of the pressure head under heavy load, the plunger pump is over 1.5 megapascals under full pressure, and the rotating speed of the turbine under no load can reach 95% of the actual flow of the pressure head, so that the basic rotating speed of the turbine under no load can be calculated.

Therefore, when the variable speed torque converter is actually manufactured, the oil duct conveying sectional area is required to be equal to or larger than the outlet area of the annular nozzle of the turbine; the input shaft (i.e. the main shaft 120 of the pump) should be connected with the engine or the clutch at the same speed for the first time, ensuring that the efficiency is not distorted; the turbine self-assembling planetary reducer 230, except for special cases, should take the impeller shaft (planetary carrier) as the output shaft, such as the rear-mounted reducer, no excessively high speed ratio is required.

In theory, all piston-type pumps can be consistent with the structural and functional configuration of the variable speed torque converter provided herein, as a preferred alternative swash plate type axial plunger pump. When the engine and the plunger pump are configured, the plunger pump is preferably selected to be matched with the engine, the property difference of the engine is compensated by changing the volume, and the effect is not changed. Hydraulic oils with low coefficients of viscosity are preferred in order to reduce the coefficient of friction of the turbine. In a specific application example, the turbine uses water as a working medium, the ideal speed ratio of the planetary reducer 230 is 3.3, and the speed ratio of the planetary reducer 230 of the turbine is between 3.4 and 3.7 because the different hydraulic oil viscosity coefficients are different and the resistance is higher than the resistance of water.

The speed-changing torque converter can be correspondingly installed with a clutch required for starting and a speed reducer required for speed limiting.

Any combination of the technical features of the above embodiments may be performed (as long as there is no contradiction between the combination of the technical features), and for brevity of description, all of the possible combinations of the technical features of the above embodiments are not described; these examples, which are not explicitly written, should also be considered as being within the scope of the present description.

The foregoing has outlined and detailed description of the present application in terms of the general description and embodiments. It should be appreciated that numerous conventional modifications and further innovations may be made to these specific embodiments, based on the technical concepts of the present application; but such conventional modifications and further innovations may be made without departing from the technical spirit of the present application, and such conventional modifications and further innovations are also intended to fall within the scope of the claims of the present application.

Claims (10)

1. The speed and torque converter is characterized by comprising a pump, a turbine, a one-way bearing, a shell and a shell base; the pump comprises a shell, a main shaft, a rotor, a runner, a liquid inlet, a liquid outlet and a valve plate, wherein the rotor is arranged in the shell, the valve plate is arranged at one end of the pump, the main shaft penetrates through the rotor, two ends of the main shaft extend out of two opposite ends of the shell respectively, one end of the main shaft penetrates through the valve plate and then is connected with the turbine through the one-way bearing, and the runner is communicated with the valve plate through the liquid outlet;

a first bin and a second bin are formed in the shell, the first bin is communicated with a liquid outlet on the valve plate to form a loop oil duct, and the one-way bearing is arranged in the first bin; the open end of the second bin is provided with a housing base, the turbine is arranged on the housing base, and the first bin is communicated with the second bin to form a supply oil duct;

the turbine comprises an inner impeller shaft connected with the unidirectional bearing, an outer impeller arranged in the middle of the inner impeller shaft, and a planetary reducer arranged at one end of the inner impeller shaft, wherein the outer impeller is arranged in the second bin; the outer impeller comprises an outer wheel body and a hollow shaft, the hollow shaft is connected with the planet carrier, and axial blades are arranged in the hollow shaft.

2. The variable speed torque converter of claim 1, wherein the pressure of the pump is independent of rotational speed and dependent on torque force, and the flow of the pump is independent of torque force and dependent on rotational speed;

the pump includes a piston pump, a plunger pump, a gear pump, or a vane pump.

3. The variable speed torque converter according to claim 1 or 2, characterized in that the pump is a swash plate type axial plunger pump, one end of which is provided with the port plate; the open end of the first bin on the shell is provided with a flange plate which is connected with the valve plate in an adapting way;

and a main shaft of the swash plate type axial plunger pump penetrates through one end of the valve plate to form a one-way bearing seat matched with the one-way bearing, and the one-way bearing seat is positioned in the first bin.

4. The variable speed torque converter according to claim 1, wherein the outer wheel body comprises an upper wheel plate and a lower wheel plate, a plurality of outer wheel plates are arranged at intervals along the circumferential edge of the outer wheel body, two ends of each outer wheel plate are respectively connected with the upper wheel plate and the lower wheel plate, the upper wheel plate, the lower wheel plate and the outer wheel plates are connected to form a fluid chamber, and an inner impeller is arranged in the fluid chamber;

the inner impeller comprises an inner wheel body and an inner impeller shaft, and the inner impeller shaft and the hollow shaft are coaxially arranged; the inner wheel body comprises an inner wheel plate, a plurality of inner wheel plates are arranged at intervals along the circumferential direction of the inner wheel plate, the lower wheel plate is provided with a discharge port, and the discharge port is positioned below the inner wheel body correspondingly;

the outer impeller is provided with an annular nozzle, the annular nozzle is located between the outer wheel piece and the inner wheel piece, the annular nozzle comprises a fluid inlet and a fluid outlet, the fluid inlet faces the outer wheel piece, and the fluid outlet faces the inner wheel piece.

5. The variable speed torque converter according to claim 4, wherein a planetary through hole is formed in the middle of the inner gear ring, the planet carrier and at least two planet gears are installed in the planetary through hole, the planet gears are installed in a meshed manner with the inner gear ring, and one end of the inner gear ring is fixedly connected with the housing base;

the inner wheel piece is provided with an inner impeller shaft, and the inner impeller shaft is provided with an inner impeller shaft which is connected with the inner impeller shaft;

the annular nozzle is arranged around the periphery of the inner wheel body, and the fluid inlet is larger than the fluid outlet;

the longitudinal cross-sectional area of the fluid inlet is at least one time greater than the longitudinal cross-sectional area of the fluid outlet;

the inner circumferential surface area of the annular nozzle is at least one time larger than the area of the discharge port;

the diameter ratio of the outer diameter of the annular nozzle to the diameter of the inner wheel body is 1.5-3;

the interval distance between the outer wheel sheets is equal to the length of the outer wheel sheets along the radial direction of the outer wheel body, and the length of the outer wheel sheets along the radial direction of the outer wheel body is 5% -20% of the diameter of the outer wheel body;

the cross section area of the discharge opening accounts for 50% -60% of the cross section area of the inner wheel body.

6. The variable speed torque converter according to claim 5, wherein the present housing is a cylindrical shell structure, one end of the present housing forms the first chamber, the other end forms the second chamber, a mounting hole is formed at a junction of the first chamber and the second chamber, the hollow shaft is penetrated in the mounting hole, a mounting cylinder is formed in the hollow shaft, the axial blades are arranged between the hollow shaft and the mounting cylinder, the axial blades comprise at least three axial blades, and the three axial blades are uniformly distributed along an inner wall of the hollow shaft;

the central axes of the hollow shaft and the mounting cylinder are coincident, and the inner impeller shaft is connected with the one-way bearing after penetrating out of the mounting cylinder.

7. The variable speed torque converter according to claim 6, wherein the housing base is a plate-like structure adapted to an end of the housing, a mount protruding toward the second chamber is formed on the housing base, the mount forms a bearing mount of the turbine, a passage allowing an inner impeller shaft to pass therethrough is formed on the bearing mount, and the inner impeller shaft is connected to the planetary reducer after passing through the bearing mount.

8. The variable speed torque converter of claim 7, wherein one end of the main shaft is connected to a power take off shaft of the engine and the other end is connected to an inner impeller shaft.

9. The variable speed torque converter according to claim 4, wherein a conveying cross-sectional area of the circuit oil passage and the supply oil passage is equal to or larger than an outlet area of the annular nozzle of the turbine.

10. The variable speed torque converter of claim 1, wherein the pump volume is less than or equal to 1/3 of the engine cylinder volume;

the speed ratio range of the planetary reducer of the turbine is 3.4-3.7.

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