Electro-hydraulic double-stirring system, control method thereof and track mortar vehicle

Abstract

The invention discloses an electro-hydraulic double-stirring system, a control method of the electro-hydraulic double-stirring system and a track mortar vehicle, and belongs to the technical field of mortar vehicles. The electro-hydraulic double-stirring system comprises a mortar tank, a stirring structure, an electric driving system and a hydraulic driving system; the hydraulic driving system comprises an axle power take-off gearbox, a transmission shaft, a first clutch, a hydraulic transmission device, a hydraulic motor and a second speed reducer, the axle power take-off gearbox is in transmission connection with the axle and is in transmission connection with the hydraulic transmission device through the transmission shaft, the transmission shaft is provided with the first clutch, and the hydraulic transmission device drives the hydraulic motor; the hydraulic motor is in transmission connection with the second speed reducer and is a constant displacement hydraulic motor; a stirring shaft of the stirring structure penetrates through the mortar tank, one end is in transmission connection with the electric driving system through a third clutch, and the other end is in transmission connection with a second speed reducer through a second clutch; the electric driving system works when the mortar vehicle does not move; the hydraulic drive system works when the speed of the mortar vehicle exceeds the starting speed.

Description

Technical Field

[0001] The invention belongs to the technical field of mortar vehicles, and in particular relates to an electric-hydraulic dual stirring system and a control method thereof, and a track mortar vehicle. Background Art

[0002] Mortar trucks are widely used as tools for transporting mortar in engineering tunnels, subway shield tunnels, and other construction operations. In order to prevent the mortar from settling and solidifying during transportation, the kinetic energy of the transport vehicle is required to continuously stir the mortar to maintain the proper activity of the mortar and meet the construction technical requirements.

[0003] In the prior art, a motor is usually used to stir a mortar truck. For example, the patent with application number CN201821058726.0 discloses an internal transmission track mortar truck, which includes a mortar truck box, a motor-driven reducer is fixed on the top of the mortar truck box, a driving shaft is rotatably connected to the motor-driven reducer, and a transmission assembly is rotatably connected to the driving shaft in a vertical direction, and a stirring assembly is connected to the end of the transmission assembly that penetrates into the mortar truck box.

[0004] For electric-driven rail mortar vehicles, the mixing system will consume the power of the machine head and reduce the mileage. If batteries are added, not only will the cost be high (the price of batteries is expensive) but the weight will also be significantly increased (the battery itself, the battery protection structure and the battery management structure, etc.; in order to ensure construction safety, the battery protection structure is heavy). In addition, electric drive also has the problems of complex wiring (a locomotive may carry multiple rail mortar vehicles, and the rail mortar vehicles all need cables to connect to the locomotive head; in addition, the rail mortar vehicles and the locomotive head must be detachably connected, and accordingly, the cables also need to be detachably connected, further complicating the structure), and prone to accidents (leakage or fire, etc.). Summary of the invention

[0005] The embodiment of the present invention provides an electric-hydraulic dual mixing system and a control method thereof and a rail mortar vehicle. The mixing system can significantly reduce the power consumption of the rail mortar vehicle and improve the mileage. The technical solution is as follows:

[0006] On the one hand, an embodiment of the present invention provides an electro-hydraulic dual mixing system, which includes a mortar tank 3, a mixing structure 4 in the mortar tank 3, an electric drive system 5 at one end of the mortar tank 3 and used to drive the mixing structure 4, and a hydraulic drive system at the other end of the mortar tank 3; the hydraulic drive system includes an axle power take-off speed increaser 6, a transmission shaft 7, a first clutch 11, a hydraulic transmission device, a hydraulic motor 9 and a second reducer 10, the axle power take-off speed increaser 6 is transmission-connected to the axle of the mortar truck and is transmission-connected to the hydraulic transmission device through the transmission shaft 7, the transmission shaft 7 is provided with a first clutch 11, the hydraulic transmission device drives the hydraulic motor 9, the hydraulic motor 9 is transmission-connected to the second reducer 10, and the hydraulic motor 9 is a quantitative hydraulic motor; the mixing The stirring shaft of structure 4 passes through the mortar tank 3, one end of which is connected to the electric drive system 5 through the third clutch 13, and the other end of which is connected to the output shaft of the second reducer 10 through the second clutch 12; the electric drive system 5 works when the mortar truck is stationary, at this time, the third clutch 13 is engaged and the second clutch 12 is disconnected; the hydraulic drive system works when the speed of the mortar truck exceeds the starting speed, at this time, the first clutch 11 is engaged, the second clutch 12 is engaged, and the third clutch 13 is disconnected; when the mortar truck is moving and the mortar truck is empty, the first clutch 11 is disconnected; when the speed of the mortar truck is less than or equal to the starting speed, the first clutch 11 is disconnected; wherein, the hydraulic transmission device can only work normally when the speed of the mortar truck is greater than the starting speed.

[0007] Among them, the first clutch 11 in the embodiment of the present invention is engaged by power on and is disconnected or engaged by a control strategy, the second clutch 12 is engaged by power off, and the third clutch 13 is engaged by power on.

[0008] Among them, the hydraulic transmission device in the embodiment of the present invention includes a hydraulic oil tank 14, a two-position three-way solenoid valve 15, a vane pump 16, an accumulator 17 and two direct-acting relief valves 18; the vane pump 16 is transmission-connected to the transmission shaft 7 and its input end is connected to the hydraulic oil tank 14 through a pipeline; the output end of the vane pump 16 is divided into two outputs, one is connected to the inlet of the hydraulic motor 9 through a pipeline, and the other is connected to an inlet of the two-position three-way solenoid valve 15 through a pipeline; the outlet of the hydraulic motor 9 is connected to the other inlet of the two-position three-way solenoid valve 15 through a pipeline, and the outlet of the two-position three-way solenoid valve 15 is connected to the hydraulic oil tank 14 through a pipeline, and the accumulator 17 is arranged on the pipeline between the vane pump 16 and the hydraulic motor 9, and the inlet and outlet of the hydraulic motor 9 are respectively connected to the hydraulic oil tank 14 through pipelines with direct-acting relief valves 18.

[0009] Furthermore, the hydraulic transmission device in the embodiment of the present invention also includes an air filter 19, a liquid level gauge 20, a thermometer 21, a heater 22, a magnetic filter 23, a differential pressure gauge 24, a cooler 25 and a pressure sensor 26. The air filter 19, the liquid level gauge 20, the thermometer 21 and the heater 22 are arranged on the hydraulic oil tank 14, the magnetic filter 23 and the cooler 25 are arranged on the pipeline between the outlet of the two-position three-way solenoid valve 15 and the hydraulic oil tank 14, the two detection ends of the differential pressure gauge 24 are respectively connected to the inlet and outlet of the magnetic filter 23 through the pipeline, and the pressure sensor 26 is arranged on the pipeline between the vane pump 16 and the hydraulic motor 9.

[0010] Furthermore, the electro-hydraulic dual stirring system in the embodiment of the present invention also includes a control system, which includes an electrical cabinet, a charging module, an electric energy conversion module, a battery, a control and execution module and a stirring speed sensor. The output end of the electrical cabinet is electrically connected to the charging module, the electric energy conversion module and the electric drive system 5 respectively, the output end of the electric energy conversion module is electrically connected to the control and execution module, the first clutch 11, the second clutch 12 and the third clutch 13, the charging module is electrically connected to the input end of the battery, the output end of the battery is electrically connected to the control and execution module, and the control and execution module is electrically connected to the control end of the first clutch 11, the stirring speed sensor and the hydraulic transmission device.

[0011] Specifically, the hydraulic transmission device in the embodiment of the present invention reaches the rated power when the speed of the mortar truck is the rated speed, and the theoretical calculated average power of the hydraulic drive system is 70-80% of the theoretical calculated average power of the electric drive system 5; the starting speed is 3km / h, and the rated speed is 5km / h; the running speed of the mortar truck is 5-8km / h; the output speed of the axle power take-off speed increaser 6 is greater than or equal to 600rpm.

[0012] On the other hand, an embodiment of the present invention also provides a rail mortar vehicle, comprising a vehicle body 1, multiple walking parts 2 at the bottom of the vehicle body 1 and the aforementioned electro-hydraulic dual mixing system, the mortar tank 3 is arranged on the vehicle body 1, and the axle power take-off speed increaser 6 is connected to the axle transmission of the nearby walking parts 2.

[0013] Specifically, a bracket 8 is provided at the lower part of the other end of the mortar tank 3 in the embodiment of the present invention, the second reducer 10 is provided on the bracket 8, and the hydraulic motor 9 is provided on the upper side of the second reducer 10; the vane pump 16, the hydraulic oil tank 14 and the cooler 25 are all provided on the vehicle body 1 and are located below the bracket 8, the hydraulic oil tank 14 and the cooler 25 are arranged side by side in the width direction of the vehicle body 1 and are located on the side of the vane pump 16 away from the mortar tank 3.

[0014] Furthermore, the rail mortar vehicle in the embodiment of the present invention further comprises a slurry discharge device, wherein the slurry discharge device and the hydraulic drive system are both located at an end of the mortar tank 3 away from the vehicle head.

[0015] On the other hand, an embodiment of the present invention further provides a control method for an electro-hydraulic dual mixing system, the method comprising: when the mortar truck stops at the slurry discharge position, the electrical cabinet is electrically connected to the power supply system; the battery is charged; the third clutch 13 is energized and engaged and the second clutch 12 is energized and disconnected, and the electric drive system 5 works to drive the mixing structure 4; when the mortar truck is moving, the third clutch 13 is powered off and disconnected, the second clutch 12 is powered off and engaged, and the battery supplies power to the hydraulic transmission device, the first clutch 11 and the control system; it is determined whether the no-mixing condition is met, if so, the first clutch 11 is disconnected, and the mixing structure 4 does not mix; otherwise, the first clutch 11 is engaged, and the hydraulic drive system drives the mixing structure 4; wherein the no-mixing condition includes that the mortar tank 3 is empty, the speed of the mortar truck is less than or equal to the starting speed, the mortar truck is within the starting time period, the expected movement time of the mortar truck is less than the set value and the no-mixing control instruction; whether the mortar tank 3 is empty is determined by the mixing speed sensor or the movement direction of the mortar truck.

[0016] The technical solution provided by the embodiment of the present invention has the following beneficial effects:

[0017] (1) Compared with electric stirring, it consumes less power (theoretically calculated to be 70-80% of the electric drive system (considering uphill and downhill slopes)). Especially in the downhill stage, the power consumption is zero, which can greatly reduce energy consumption.

[0018] (2) For electric vehicles, compared with the prior art, this patent will reduce the consumption of locomotive reserve power and ensure the cruising range of electric locomotives. The weight added by this hydraulic drive system is less than the weight added by the battery. For internal combustion vehicles (which also need to carry more fuel), they must be equipped with an external generator, which will increase the weight of the internal combustion vehicle, which will inevitably increase the engine power, so the manufacturing cost and use cost of the whole vehicle will increase to a certain extent.

[0019] (3) When the rail mortar car goes downhill, the hydraulic drive system consumes the gravity work of the rail mortar car, which can be understood as zero consumption of the machine head; at the same time, it can also be understood as resistance (equivalent to damping) to prevent the rail mortar car from going too fast, ensure the speed of the rail mortar car is stable, and reduce the use of brakes (which also consumes power). The greater the change in track height, the more obvious the advantage of this system will be.

[0020] (4) Avoiding cable (usually 380V) routing simplifies the structure and avoids risks such as leakage and fire.

[0021] (5) The mixing speed of the hydraulic drive system is stable and does not change with the running speed of the rail mortar car.

[0022] (6) It can be installed at the same end as the pulp discharge device, utilizing the space next to the pulp discharge device without the need to set up additional installation space.

[0023] In short, the mixing system can significantly reduce the power consumption of the rail mortar vehicle and improve the mileage. BRIEF DESCRIPTION OF THE DRAWINGS

[0024] Figure 1 is a schematic structural diagram of a rail mortar vehicle provided by an embodiment of the present invention;

[0025] Figure 2 It is the principle diagram of hydraulic transmission device;

[0026] Figure 3 It is the principle block diagram of the control system.

[0027] In the figure: 1 body, 2 walking part, 3 mortar tank, 4 mixing structure, 5 electric drive system, 6 axle power take-off speed increaser, 7 transmission shaft, 8 bracket, 9 hydraulic motor, 10 second reducer, 11 first clutch, 12 second clutch, 13 third clutch, 14 hydraulic oil tank, 15 two-position three-way solenoid valve, 16 vane pump, 17 accumulator, 18 direct-acting overflow valve, 19 air filter, 20 level gauge, 21 thermometer, 22 heater, 23 magnetic filter, 24 differential pressure gauge, 25 cooler, 26 pressure sensor. DETAILED DESCRIPTION

[0028] In order to make the objectives, technical solutions and advantages of the present invention more clear, the present invention will be further described in detail below with reference to the accompanying drawings.

[0029] Example 1

[0030] See also Figure 1-3 Embodiment 1 provides an electric-hydraulic dual stirring system, which includes a mortar tank 3, a stirring structure 4, an electric drive system 5, a hydraulic drive system, etc. The electric drive system 5 and the hydraulic drive system are respectively arranged at both ends of the mortar tank 3, and one or both of them do not drive the stirring structure 4. The electric drive system 5 includes a drive motor and a first reducer, etc.

[0031] Among them, the hydraulic drive system includes an axle power take-off speed increaser 6, a transmission shaft 7, a first clutch 11, a hydraulic transmission device, a hydraulic motor 9, a second reducer 10 and a control system. The axle power take-off speed increaser 6 is connected to the axle of the mortar car, and is connected to the hydraulic transmission device through the transmission shaft 7. It is used to increase the speed (the rail mortar car runs very slowly) to reach the minimum speed of the hydraulic transmission device. The transmission shaft 7 is provided with a first clutch 11, and the hydraulic transmission device drives the hydraulic motor 9, and the hydraulic motor 9 is connected to the second reducer 10. The hydraulic motor 9 is a quantitative hydraulic motor. The stirring structure 4 is arranged in the mortar tank 3, and its stirring shaft passes through the mortar tank 3. One end of the stirring structure 4 is connected to the electric drive system 5 through the third clutch 13, and the other end of the stirring structure 4 is connected to the output shaft of the second reducer 10 through the second clutch 12. The first clutch 11 is connected in a power-on manner and is disconnected or connected through a control strategy. The second clutch 12 is connected in a power-off manner, and the third clutch 13 is connected in a power-on manner. The first clutch 11 is disconnected as required (such as low speed, no-load, etc.) to reduce the impact on the hydraulic transmission device.

[0032] Among them, the electric drive system 5 works when the mortar truck is stationary. At this time, the third clutch 13 is engaged and the second clutch 12 is disconnected. The hydraulic drive system works when the speed of the mortar truck exceeds the starting speed. At this time, the first clutch 11 is engaged, the second clutch 12 is engaged, and the third clutch 13 is disconnected. When the mortar truck is moving and the mortar truck is empty, the first clutch 11 is disconnected. When the speed of the mortar truck is less than or equal to the starting speed, the first clutch 11 is disconnected. In other cases where stirring is not required, the first clutch 11 is disconnected. Among them, the hydraulic transmission device can only work normally when the speed of the mortar truck is greater than the starting speed.

[0033] The hydraulic transmission device in the embodiment of the present invention includes a hydraulic oil tank 14, a two-position three-way solenoid valve 15, a vane pump 16, an accumulator 17, two direct-acting relief valves 18, an air filter 19, a level gauge 20, a thermometer 21, a heater 22, a magnetic filter 23, a differential pressure gauge 24, a cooler 25, and a pressure sensor 26. The vane pump 16 is connected to the transmission shaft 7 in a transmission manner, and its input end is connected to the hydraulic oil tank 14 through a pipeline. The output end of the vane pump 16 is divided into two outputs, one of which is connected to the inlet of the hydraulic motor 9 through a pipeline, and the other is connected to one inlet of the two-position three-way solenoid valve 15 through a pipeline. The outlet of the hydraulic motor 9 is connected to the other inlet of the two-position three-way solenoid valve 15 through a pipeline; the outlet of the two-position three-way solenoid valve 15 is connected to the hydraulic oil tank 14 through a pipeline. The accumulator 17 is arranged on the pipeline between the vane pump 16 and the hydraulic motor 9, and the inlet and outlet of the hydraulic motor 9 are respectively connected to the hydraulic oil tank 14 through pipelines with direct-acting relief valves 18. The air filter 19, the level gauge 20, the thermometer 21 and the heater 22 are arranged on the hydraulic oil tank 14, the magnetic filter 23 and the cooler 25 are arranged on the pipeline between the outlet of the two-position three-way solenoid valve 15 and the hydraulic oil tank 14, the two detection ends of the differential pressure gauge 24 are respectively connected to the inlet and outlet of the magnetic filter 23 through the pipeline, and the pressure sensor 26 is arranged on the pipeline between the vane pump 16 and the hydraulic motor 9. The stirring direction is controlled by controlling the two-position three-way solenoid valve 15.

[0034] In this patent, the axle speed will cause a large fluctuation in the input speed as the vehicle speed increases or decreases, which has an adverse effect on the hydraulic drive. Therefore, a quantitative motor (in conjunction with other structures) is used in the hydraulic drive part to adjust the torque and speed required for stirring through the quantitative motor. No matter how high the vehicle speed is, it will not affect the stirring speed. At the same time, an accumulator is added to the pipeline to effectively prevent damage to the hydraulic components caused by the impact caused by the locomotive when shifting gears.

[0035] Further, the control system in the embodiment of the present invention includes an electrical cabinet, a charging module, an electric energy conversion module, a battery, a control and execution module, a stirring speed sensor, etc. The control and execution module includes a PLC and an execution unit, a processing unit, etc. The output end of the electrical cabinet is electrically connected to the charging module, the electric energy conversion module and the electric drive system 5 respectively, the output end of the electric energy conversion module is electrically connected to the control and execution module, the first clutch 11, the second clutch 12 and the third clutch 13, the charging module is electrically connected to the input end of the battery, the output end of the battery is electrically connected to the control and execution module, the control and execution module is electrically connected to the control end of the first clutch 11 (powering the first clutch 11 at the same time), the stirring speed sensor and the hydraulic transmission device (for the electronic control unit and sensors therein, such as the two-position three-way solenoid valve 15, the pressure sensor 26, etc.).

[0036] Specifically, the hydraulic transmission device in the embodiment of the present invention reaches the rated power when the speed of the mortar truck is the rated speed, and the theoretical calculated average power of the hydraulic drive system (measured at 50% uphill) is 70-80% of the theoretical calculated average power of the electric drive system 5. Among them, the starting speed is 3km / h and the rated speed is 5km / h. The running speed of the mortar truck is 5-8km / h; the output speed of the axle power take-off speed increaser 6 is greater than or equal to 600rpm. The mixing structure 4 is an anchor blade mixing structure, the impeller diameter Di is 1.0-1.2m (corresponding to the tank diameter Dt of 1.38m and the depth of 4.2m), and the number of sections is 2.

[0037] Example 2

[0038] Embodiment 2 provides a rail mortar vehicle, including a vehicle body 1, a slurry discharge device (discharging mortar outward), a plurality of (specifically two) running parts 2 at the bottom of the vehicle body 1, and the electro-hydraulic dual mixing system disclosed in Embodiment 1, etc., a mortar tank 3 is arranged on the vehicle body 1, and an axle power take-off speed increasing box 6 is connected to the axle of the nearby running part 2. The slurry discharge device and the hydraulic drive system are both located at one end of the mortar tank 3 away from the front of the vehicle (both will occupy a large space).

[0039] Specifically, a bracket 8 is provided at the lower part of the other end of the mortar tank 3 in the embodiment of the present invention, a second reducer 10 is provided on the bracket 8, and a hydraulic motor 9 is provided on the upper side of the second reducer 10. The vane pump 16, the hydraulic oil tank 14 and the cooler 25 are all provided on the vehicle body 1 and are located below the bracket 8, and the hydraulic oil tank 14 and the cooler 25 (the hydraulic oil tank 14 and the cooler 25 both occupy a large space, and other structures are provided according to space requirements) are provided side by side in the width direction of the vehicle body 1 and are located on the side of the vane pump 16 away from the mortar tank 3.

[0040] Example 3

[0041] Embodiment 3 provides a rail mortar vehicle, and its structure is basically the same as that of Embodiment 2, except that: the vehicle body 1 in the embodiment of the present invention is arranged in the front-to-back direction, the mortar tank 3 is arranged in the front-to-back direction, the electric drive system 5 is arranged at the front end of the mortar tank 3, and the hydraulic drive system is located at the rear end of the mortar tank 3. The transmission shaft 7 is arranged in the front-to-back direction. The vane pump 16 is located directly below the bracket 8. The hydraulic oil tank 14 and the cooler 25 are arranged side by side on the left and right, and are located behind the vane pump 16, which is arranged at the rear end of the vehicle body 1. The axle power take-off speed increaser 6 is connected to the axle transmission of the walking part 2 at the rear end.

[0042] Example 4

[0043] Embodiment 4 provides a track mortar vehicle, the structure of which is basically the same as that of Embodiment 2, except that the mixing structure 4 in this embodiment is an anchor blade mixing structure. The theoretical calculated power of the hydraulic drive system is 4.72KW. The power of the electric drive system is 6.29KW.

[0044] 1. Design and power of stirring structure 4:

[0045] 1.1 Selection of stirring structure 4:

[0046] Anchor impellers are cheaper than propeller impellers. With the same diameter and speed, the power consumed by anchor impellers is only about 2 / 3 of that of propeller impellers. According to the analysis of usage, the ratio of impeller diameter to tank diameter is 0.7-0.9 for stirring low-viscosity fluids and 0.8-0.95 for stirring high-viscosity fluids. The suitable speed range is 10-50r / min, and the applicable viscosity range is from low viscosity to 200-300Pa.s.

[0047] 1.2 Design of stirring impeller:

[0048] In addition to selecting the impeller shape that meets the mixing purpose, the impeller diameter, number of stages and impeller installation position should also be considered. If these conditions are not considered properly, the mixing effect will be seriously affected.

[0049] 1.3 Design of impeller diameter:

[0050] When designing the impeller diameter, the ratio of the impeller diameter to the mixing tank diameter can be considered based on geometric similarity conditions. If it is lower than the lower limit of the range, local flow strength will be uneven, and in severe cases, mixing dead corners will occur.

[0051] The impeller diameter Di is in close fit with the tank body, that is, the tank body diameter Dt is 1.38m and the impeller diameter Di is 1.1m, which meets the design conditions of the anchor impeller.

[0052] 1.4 Segment design:

[0053] The number of impeller sections is related to the ratio of the liquid depth in the tank to the diameter of the tank. It is usually hoped that the ratio of the liquid depth to the tank diameter is 1±0.2. At this ratio, if it is a low-viscosity fluid, a single-section impeller is sufficient. For situations where the ratio of the liquid depth to the tank diameter exceeds this range, one section can be added. However, for fluids with a viscosity of several Pascal seconds, even at this ratio, two sections are required due to the poor fluidity caused by increased viscosity. The stirring of fluids with viscosities above this requires three sections or an appropriate increase in the number of sections. When the viscosity of the liquid to be stirred is greatly different from the relative density, in addition to paying attention to the installation position of the impeller, it is also necessary to consider increasing the number of impeller sections.

[0054] The design depth of the mixing tank is 4.2m, and the ratio of the liquid depth of the mixing tank to the diameter of the tank is about 3, that is, the design number of sections is 2.

[0055] 1.5 Specifications of stirring medium:

[0056] This rail mortar truck is mainly used for synchronous grouting construction in subway shield construction. The mixing medium is based on the ratio provided by the on-site construction unit. The density of the mixing medium is 1850kg / m 3 , the ash-sand ratio should be around 1:2, and the viscosity of the stirring medium should be 250mPa.s.

[0057] 1.6 Calculation of stirring power:

[0058] After determining the impeller shape, diameter and number of revolutions, the power required for stirring can be calculated. The stirring power is calculated by the following formula:

[0059]

[0060] Formula 1:

[0061] Where: H—stirring liquid depth (m)—4.2m;

[0062] Dt—mixing tank diameter (m)—1.38m;

[0063] Di—impeller diameter (m)—1.1m;

[0064] b—impeller blade width (m)—0.625m [(width of one blade (0.125m) × number of blades (5) × number of segments (2) / 2];

[0065] θ—blade installation angle—30°;

[0066] d--Stirring medium density—1850kg / m 3 ;

[0067] μ—stirring medium viscosity—250mPa.s;

[0068] g—gravity conversion factor—9.8 m / s 2 ;

[0069] n—rotation speed—12r / min;

[0070] Np—power factor;

[0071] Re—Reynolds number;

[0072] PA—stirring power;

[0073] PB—motor driving power;

[0074] Z—total efficiency, generally 0.75;

[0075] Np is affected by the impeller shape, geometric conditions, and baffle conditions, and is a function of the Reynolds number Re. The stirring Reynolds number Re can be given by the following formula:

[0076] Formula 2:

[0077] Calculation shows that Re=1.79.

[0078] When there is no baffle and Re < 300, the NP value can be calculated by the following formula:

[0079] Nagata formula

[0080]

[0081] in:

[0082] The calculation results show that NP = 63.74

[0083] Substituting into formula 1, the stirring power PA = 4.72KW can be obtained.

[0084] 2. Calculation of hydraulic drive system power:

[0085] 2.1 Calculation of hydraulic motor displacement:

[0086] According to the principle that the output torque of the second reducer is equal to the output torque of the first reducer and the low-speed stirring during transportation, the selection calculation is carried out, and the output torque of the second reducer is 6000N..m. When the locomotive speed is 3km / h, the hydraulic pump reaches the minimum working speed, and the rated working speed is reached at 5km / h. The long-term operating speed of the locomotive is 5-8km / h.

[0087] The reduction ratio of the second reducer is the same as that of the first reducer, which is 120:1. The input torque of the reducer (i.e. the motor output torque) can be obtained as follows:

[0088] T0 = ​​6000 / 120 = 50 N.m;

[0089] According to the setting, the minimum output speed of the agitator shaft is 6rpm (vehicle speed 5km / h), then the input speed of the reducer (i.e. the motor output speed):

[0090] nin=6×120=720rpm.

[0091]

[0092] In the above formula: p = 16Mpa

[0093] ηm=90%

[0094] From this calculation, we can conclude that: q0=22ml / r.

[0095] 2.2 Selection of hydraulic motor:

[0096] The parameter selection hydraulic motor model is A6V28EP12FP2-22, the displacement range is 8.1-28.1ml / r, and the output torque range is 18.564-64.4Nm.

[0097] 2.3 Calculation of hydraulic motor power:

[0098] Based on the above, the output power of the hydraulic motor at 5km / h can be calculated:

[0099] P0=pQ0η

[0100] =16×106×0.25×10-3×0.9=3600w;

[0101] Motor input power No = P0 / η

[0102] =3600 / 0.9=4000W;

[0103] In the above formula, η is the mechanical efficiency.

[0104] 2.4 Selection of vane pump:

[0105] The motor output speed is 720-900rpm, corresponding to the stirring shaft output speed of 6-7.5rpm, which meets the requirements of low-speed stirring.

[0106] The motor flow rate is 20-24L / min depending on the motor displacement.

[0107] According to the motor flow and input speed range, the vane pump model A37 is selected. The variable displacement of the vane pump is 27ml / r and 17ml / r. The speed range is 600-1800rpm, the flow range is 17.76-53.28L / min, and the volumetric efficiency is 80%.

[0108] 2.5 Calculation of axle power take-off speed increaser:

[0109] Pump input torque:

[0110]

[0111] In the above formula: p = 16Mpa, ηm = 90%, q0 = 27ml / r.

[0112]

[0113] It can be seen from the above formula that the output torque of the axle power take-off speed increaser is ≥76.43Nm.

[0114] 2.6 Calculation of mortar truck load:

[0115] When the speed of the mortar truck is 5 km / h, the corresponding axle speed is 66.3 rpm; therefore, the axle power take-off speed increaser needs to increase the speed to 1000 rpm to meet the minimum speed requirement of the pump. The speed ratio of the speed increaser is 1:15. At this time, the torque required for the axle to drive the pump is:

[0116] Mi=Ti×i=76.43×15=1146.5Nm,

[0117] At this time, the load on the axle is: F = Mi / r = 1146.5 / 0.2 = 5732.5N;

[0118] In the above formula: r: wheel radius.

[0119] 2.7 Calculation of power consumption of mortar truck mixing:

[0120] Therefore, the locomotive load power is:

[0121] N1=Fv / 3.6=5.732.5×5 / 3.6=7.96kW;

[0122] In the above formula: v = 5km / h;

[0123] According to the above calculation, when the speed is 8km / h and the pump displacement is 17ml / r, the locomotive load power is N2=8.02kW.

[0124] According to the construction industry and mining industry, the general energy consumption calculation is based on the ratio of uphill and downhill, each accounting for 50%. The hydraulic mixing system is driven by the grouping sliding force in the downhill stage, and does not need to consume locomotive energy. Therefore, the average energy consumption of the hydraulic mixing of the power take-off box is:

[0125] N0=N2 / 2=4.01kW.

[0126] 3. Calculation of driving power of electric drive system:

[0127] The electric drive system is mainly driven by an electric motor. In addition to considering factors such as power supply and operating conditions, the most important aspect of the motor selection is to determine the driving power and select a suitable motor (in addition to electric motors, hydraulic and pneumatic motors are also used). The capacity of the motor should include the power required for stirring, the power loss of the mixer and the power loss of the reducer. In addition, calculation errors and power changes that may be caused by changes in operating conditions should also be considered. Usually, the power required for stirring only accounts for 60%-70% of the total driving power. The power loss of the mixer and reducer body accounts for about 10%-20%. The surplus power is about 20%. Select the motor capacity accordingly.

[0128] P B =P A / Z

[0129] Calculation shows that the stirring power PA is 4.72KW and the motor power PB is 6.29KW.

[0130] 4.72 / 6.29=75.04%.

[0131] IV. Conclusion

[0132] When the electric drive system is performing walking mixing, it works throughout the entire process without being affected by the slope, and its energy consumption is higher than the energy consumption required for hydraulic mixing with a power take-off box.

[0133] Example 5

[0134] Embodiment 5 provides a control method for an electro-hydraulic dual stirring system, the method comprising:

[0135] When the mortar truck stops at the slurry discharge position, the electrical cabinet is electrically connected to the power supply system; the battery is charged; the third clutch 13 is energized and engaged and the second clutch 12 is energized and disconnected, and the electric drive system 5 works to drive the stirring structure 4.

[0136] When the mortar truck is moving, the third clutch 13 is powered off and disconnected, the second clutch 12 is powered off and engaged, and the battery supplies power to the hydraulic transmission device, the first clutch 11 and the control system. It is determined whether the non-stirring condition is met. If so, the first clutch 11 is disconnected and the stirring structure 4 does not stir; otherwise, the first clutch 11 is engaged and the hydraulic drive system drives the stirring structure 4.

[0137] Among them, the no-stirring conditions include that the mortar tank 3 is empty, the speed of the mortar truck is less than or equal to the starting speed, the mortar truck is within the starting time period, the mortar truck is expected to move less than the set value (such as the mortar truck is expected to move less than 0.5h, and the mortar will not coagulate during this time period) and no-stirring control instructions (such as manually input control instructions, etc.). Of course, there can be other no-stirring conditions. Whether the mortar tank 3 is empty is judged by the stirring speed sensor or the movement direction of the mortar truck (such as the mortar truck running in reverse).

[0138] The above description is only a preferred embodiment of the present invention and is not intended to limit the present invention. Any modifications, equivalent substitutions, improvements, etc. made within the spirit and principle of the present invention should be included in the protection scope of the present invention.

Claims

1. An electric-hydraulic dual stirring system, comprising a mortar tank (3), a stirring structure (4) in the mortar tank (3), and an electric drive system (5) at one end of the mortar tank (3) for driving the stirring structure (4); characterized in that: Also included is a hydraulic drive system at the other end of the mortar tank (3); The hydraulic drive system comprises an axle power take-off speed increasing box (6), a transmission shaft (7), a first clutch (11), a hydraulic transmission device, a hydraulic motor (9) and a second reducer (10); the axle power take-off speed increasing box (6) is transmission-connected to the axle of the mortar truck and is transmission-connected to the hydraulic transmission device via the transmission shaft (7); the transmission shaft (7) is provided with a first clutch (11); the hydraulic transmission device drives the hydraulic motor (9); the hydraulic motor (9) is transmission-connected to the second reducer (10); the hydraulic motor (9) is a quantitative hydraulic motor; the stirring shaft of the stirring structure (4) passes through the mortar tank (3); one end of the stirring shaft is transmission-connected to the electric drive system (5) via the third clutch (13); and the other end of the stirring shaft is transmission-connected to the output shaft of the second reducer (10) via the second clutch (12); The electric drive system (5) works when the mortar truck is stationary, at which time the third clutch (13) is engaged and the second clutch (12) is disconnected; the hydraulic drive system works when the speed of the mortar truck exceeds the starting speed, at which time the first clutch (11) is engaged, the second clutch (12) is engaged, and the third clutch (13) is disconnected; when the mortar truck is moving and empty, the first clutch (11) is disconnected; when the speed of the mortar truck is less than or equal to the starting speed, the first clutch (11) is disconnected; Among them, the hydraulic transmission device can only work normally when the speed of the mortar truck is greater than the starting speed.

2. The electro-hydraulic dual stirring system according to claim 1, characterized in that: The first clutch (11) is coupled in an energized manner and is disconnected or coupled through a control strategy, the second clutch (12) is coupled in an off-power manner, and the third clutch (13) is coupled in an energized manner.

3. The electro-hydraulic dual stirring system according to claim 1, characterized in that: The hydraulic transmission device comprises a hydraulic oil tank (14), a two-position three-way solenoid valve (15), a vane pump (16), an accumulator (17) and two direct-acting relief valves (18); the vane pump (16) is connected to the transmission shaft (7) in a transmission manner and its input end is connected to the hydraulic oil tank (14) through a pipeline; the output end of the vane pump (16) is divided into two output paths, one path is connected to the inlet of the hydraulic motor (9) through a pipeline, and the other path is connected to one inlet of the two-position three-way solenoid valve (15) through a pipeline; the outlet of the hydraulic motor (9) is connected to the other inlet of the two-position three-way solenoid valve (15) through a pipeline, and the outlet of the two-position three-way solenoid valve (15) is connected to the hydraulic oil tank (14) through a pipeline; the accumulator (17) is arranged on the pipeline between the vane pump (16) and the hydraulic motor (9), and the inlet and outlet of the hydraulic motor (9) are respectively connected to the hydraulic oil tank (14) through pipelines with direct-acting relief valves (18).

4. The electro-hydraulic dual stirring system according to claim 3, characterized in that: The hydraulic transmission device further comprises an air filter (19), a liquid level gauge (20), a thermometer (21), a heater (22), a magnetic filter (23), a differential pressure gauge (24), a cooler (25) and a pressure sensor (26); the air filter (19), the liquid level gauge (20), the thermometer (21) and the heater (22) are arranged on the hydraulic oil tank (14); the magnetic filter (23) and the cooler (25) are arranged on a pipeline between the outlet of the two-position three-way solenoid valve (15) and the hydraulic oil tank (14); two detection ends of the differential pressure gauge (24) are respectively connected to the inlet and outlet of the magnetic filter (23) through pipelines; and the pressure sensor (26) is arranged on a pipeline between the vane pump (16) and the hydraulic motor (9).

5. The electro-hydraulic dual stirring system according to claim 1, characterized in that: The electric-hydraulic dual stirring system further comprises a control system, the control system comprising an electrical cabinet, a charging module, an electric energy conversion module, a storage battery, a control and execution module and a stirring speed sensor, the output end of the electrical cabinet being electrically connected to the charging module, the electric energy conversion module and the electric drive system (5) respectively, the output end of the electric energy conversion module being electrically connected to the control and execution module, the first clutch (11), the second clutch (12) and the third clutch (13), the charging module being electrically connected to the input end of the storage battery, the output end of the storage battery being electrically connected to the control and execution module, and the control and execution module being electrically connected to the control end of the first clutch (11), the stirring speed sensor and the hydraulic transmission device.

6. The electro-hydraulic dual stirring system according to claim 1, characterized in that: The hydraulic transmission device reaches the rated power when the speed of the mortar truck is the rated speed, and the theoretical calculated average power of the hydraulic drive system is 70-80% of the theoretical calculated average power of the electric drive system (5); the starting speed is 3km / h, and the rated speed is 5km / h; the running speed of the mortar truck is 5-8km / h; the output speed of the axle power take-off speed increaser (6) is greater than or equal to 600rpm.

7. A rail mortar vehicle, comprising a vehicle body (1) and a plurality of running parts (2) at the bottom thereof; characterized in that: It also includes the electric-hydraulic dual mixing system as claimed in claim 4, wherein the mortar tank (3) is arranged on the vehicle body (1), and the axle power take-off speed increasing box (6) is connected to the axle transmission of the nearby walking part (2).

8. The rail mortar vehicle according to claim 7, characterized in that: A bracket (8) is provided at the lower part of the other end of the mortar tank (3), the second reducer (10) is provided on the bracket (8), and the hydraulic motor (9) is provided on the upper side of the second reducer (10); the vane pump (16), the hydraulic oil tank (14) and the cooler (25) are all provided on the vehicle body (1) and are located below the bracket (8); the hydraulic oil tank (14) and the cooler (25) are arranged side by side in the width direction of the vehicle body (1) and are located on the side of the vane pump (16) away from the mortar tank (3).

9. The rail mortar vehicle according to claim 7, characterized in that: The rail mortar vehicle also comprises a slurry discharge device, wherein the slurry discharge device and the hydraulic drive system are both located at an end of the mortar tank (3) away from the vehicle head.

10. The control method of the electric-hydraulic dual stirring system according to claim 5, characterized in that: The method comprises: When the mortar truck stops at the mortar discharge position, the electrical cabinet is electrically connected to the power supply system; the battery is charged; the third clutch (13) is energized and engaged and the second clutch (12) is energized and disconnected, and the electric drive system (5) works to drive the stirring structure (4); When the mortar truck is moving, the third clutch (13) is powered off and disconnected, the second clutch (12) is powered off and engaged, and the battery supplies power to the hydraulic transmission device, the first clutch (11) and the control system; it is determined whether the no-stirring condition is met, and if so, the first clutch (11) is disconnected and the stirring structure (4) does not stir; otherwise, the first clutch (11) is engaged and the hydraulic drive system drives the stirring structure (4); wherein the no-stirring condition includes that the mortar tank (3) is empty, the speed of the mortar truck is less than or equal to the starting speed, the mortar truck is within the starting time period, the estimated movement time of the mortar truck is less than a set value and a no-stirring control instruction; and whether the mortar tank (3) is empty is determined by a stirring speed sensor or the movement direction of the mortar truck.

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