RU2488502C2 - Method of controlling machine power recovery and device to this end - Google Patents

Abstract

FIELD: transport.

SUBSTANCE: invention relates to automotive industry. Proposed method consists in engaging flywheel with transmission via gearing with variable gear ratio subject to transmission rpm. Gear ratio is varied automatically with the help of planetary differential 5 with number of degrees of freedom equal to 2 which engages flywheel 12, traction motor 6, control reversible electric machine 13 and transmission 7. Application of controlled clutch allows ruling out power losses in machine outage.

EFFECT: complete recovery of braking energy by varying gear ratio by recommended relationship.

5 cl, 3 dwg

Description

FIELD OF TECHNOLOGY

The invention relates to the field of recovery of braking energy of transport vehicles, such as hybrid power plants with internal combustion engines and electric vehicles, as well as to devices for implementing this technology.

BACKGROUND OF THE INVENTION

A known method and control device for energy recovery of a machine using a speed variator connecting a flywheel with a transmission, which are described in the book [1] (Gulia N.V. "Inertia" - M .: Nauka, 1982. 152 p.). In [2] (Flyweel drave system "Garratt corporation" (United States patent 4,233,858 Nov. 18. 1980 PCT / US 019778 WO 2008/033378 App. No. 754, 597 Dec.27, 1976 Int cl3 F16h 37/06)) an analogue of the machine energy recovery control device is given

A known way to control the energy recovery of a machine is to change the gear ratio of the variator Pvar, located in the kinematic chain between the transmission of the machine and the flywheel. However, the optimal dependence of the change in the gear ratio of the variator is not given in [1, 2]. Experimental studies were carried out by the author [1] on a tape variator with an uncontrolled change in the gear ratio, depending on the thickness of the tape, which did not provide a constant total kinetic energy of the machine and flywheel transmission and complete recovery of the braking energy. Therefore, according to the known method, the optimal dependence of the change in the gear ratio of the variator and full recovery is impossible. Improvement of the known method of managing energy recovery by the author [1] was not carried out.

The known control device for energy recovery of the machine does not fundamentally implement and does not maintain a constant total value of the kinetic energy of the transmission of the machine and the flywheel since it partially converts part of the mechanical energy into electrical energy and transfers it to an electric battery. The known control device for recovering energy from a machine does not fundamentally realize complete recovery of braking energy, since it is not possible to optimally change the gear ratio of a variator without creating an automatic control system based on the principles of self-alignment of the kinetic energy of the transmission of the machine and the flywheel, which would ensure a constant total value of the kinetic energy of the transmission and flywheel.

The scheme of the known device for controlling energy recovery of a machine manufactured by Garratt corporation (USA) [1, 2] includes a traction electric motor and a transmission connected by a gear transmission with a constant gear ratio with one degree of mobility, as well as a control reversible electric machine, a flywheel and a planetary a differential with two degrees of mobility, consisting of two central gears (of which one central gear with an internal tooth), and the other central gear with an external tooth It is called the central gear, as well as from the carrier and the satellite located on the carrier and meshed with two central gears, the flywheel being connected to the central gear. With such a combination of links, it is impossible to create a system of automatic control on the principles of self-alignment of the kinetic energy of the transmission of the machine and the flywheel, which would provide a constant total value of the kinetic energy of the transmission of the machine and the flywheel. The energy flow to the flywheel and vice versa is controlled through a planetary differential with two degrees of mobility w = 2, consisting of two central gears (of which one central gear with an internal tooth), and the other central gear with an external tooth is called the central gear, and also from a carrier and a satellite located on the carrier and meshed with two central gears, the flywheel being connected to the central gear. A powerful electric battery serves to accumulate energy during braking of the machine and to power the traction motor during acceleration and during steady motion. Moreover, only part of the braking energy is stored in the flywheel, and the energy from the electric accumulator is spent both on overcoming the forces of useful resistance to movement and on controlling the planetary differential using a control reversible electric machine. To control the known device for energy recovery of the machine, a stepless smooth change mechanism is used, including a traction motor and transmission, interconnected by a gear transmission with a constant gear ratio with one degree of mobility, including also a control reversible electric machine, a flywheel and a planetary differential with two degrees of mobility w = 2, consisting of two central gears (of which one central gear with an internal tooth), and the other sweeping with the external gear teeth called central pinion and the satellite from the carrier and located on the carrier and engaged with two central gears, wherein the flywheel is connected to the central gear. However, the optimal change in the gear ratio of the variator is not given in [1, 2]. Experimental studies were carried out by the author [1], but they did not provide control on the principles of self-alignment of the kinetic energy of the transmission of the machine and the flywheel, which would provide a constant total value of the kinetic energy of the transmission of the machine and the flywheel. Thus, with the known connection of the links [1, 2], it is impossible to create an automatic control system based on the principles of self-alignment of the kinetic energy of the transmission of the machine and the flywheel, which would ensure a constant total value of the kinetic energy of the transmission of the machine and the flywheel.

SUMMARY OF THE INVENTION

The aim of the present invention is to provide such a device that would ensure complete recovery of braking energy by automatically operating in any driving conditions of the machine. This goal is achieved by the fact that the exchange of kinetic energy between the flywheel and the transmission of the machine is carried out by changing the gear ratio of the planetary differential, which connects the transmission, electric motor and flywheel. The change in the gear ratio of the kinematic chain of the planetary differential, which connects the transmission and the flywheel, is carried out by using the proposed method of maintaining a constant total value of the kinetic energy of the transmission of the machine and the flywheel.

This requires that the flywheel can fully accumulate the kinetic energy of the machine’s transmission. This condition is fulfilled for a certain necessary ratio of the reduced moments of inertia of the machine and the flywheel, which is found from the kinetic energy equation and depends on the maximum values of the rotation speeds of 1 flywheel (ω ₁ ) _max and the drive link 2 of the transmission (ω ₂ ) _max

$$\frac{J_2}{J_{\mathrm{one}}}={\left(\frac{{\omega }_{\mathrm{one}\mathrm{<figure-callout\; id="2"\; label="max\; \omega "\; filenames="00000008.png"\; state="\{\{state\}\}">max\; </figure-callout>}}}{{\omega }_{}}\right)}^2,\text{(one)}$$

where J ₁ and J ₂ are the reduced moments of inertia of the flywheel and the machine;

The search for the optimal law of variation of the transfer function of the variator, necessary to eliminate kinetic energy losses during braking, is carried out according to the equation of conservation of energy of a machine with a flywheel battery, taking into account the above necessary ratio of moments of inertia according to the equation of conservation of energy of the machine. The expression of the optimal law of variation of the transfer function of the variator depending on the ratio of the current ω _tr and the maximum (varieties of speeds of the link to bring the transmission of the machine for a two-mass model of the machine has the form

$$U_{\mathrm{at}\mathrm{but}R}={\{{[{({\omega }_{m\mathrm{but}x\mathrm{about}\mathrm{at}})}_{\max }/{\omega }_{tR}]}^2-\mathrm{one}\}}^{\mathrm{one}/2}\text{(2)}$$

A known method of controlling energy recovery of a machine, which consists in changing the gear ratio of the variator U _var in the kinematic chain between the transmission of the machine and the flywheel.

сопровождается и скорость вращения маховика ω_махов A method for controlling energy recovery of a machine is proposed, characterized in that a constant total value of the kinetic energy of the transmission of the machine and the flywheel is provided by changing the gear ratio of the variator U _var according to the relation that relates the speed of rotation of the transmission $${\stackrel{\text{'}\text{'}}{\omega }}_{tR}$$

accompanied by the rotation speed of the flywheel ω _max

_Var U = {[(ω _{swings) max} / ω _tr] ^{2} 1/2} -1

1. The control method of energy recovery of the machine, which consists in changing the gear ratio of the variator U _var in the kinematic chain between the transmission of the machine and the flywheel, characterized in that a constant total value of the kinetic energy of the transmission of the machine and the flywheel is provided by changing the gear ratio of the variator U _var according to the relation that the transmission rotation speed ω _{tr is} accompanied by the rotation speed of the flywheel ω _max

U _Var = {[(ω _{swings) max} / (ω _mp] ² -1} ^1/2

The essential features of the proposed method, which coincide with the features of the analogue, are that both methods of controlling the energy recovery of the machine consist in changing the gear ratio of the variator U _var in the kinematic chain between the transmission of the machine and the flywheel.

Significant differences of the proposed method, which do not coincide with the characteristics of the analogue, consist in the fact that they provide a constant total value of the kinetic energy of the transmission of the machine and the flywheel by changing the gear ratio of the variator U _var according to the relation that links the rotation speed of the transmission ω _{tr is} accompanied by the rotation speed of the flywheel ω _swings

_Var U = {[(ω _{swings) max} / (ω _mp] ^{2} 1/2} -1

Additional differences of the proposed method, which do not coincide with the characteristics of the analogue, are that the rotation speeds of the input and output links of the variator in the kinematic chain between the transmission of the machine and the flywheel have opposite directions. This difference is significant, since the opposite directions of the speed of rotation of the input and output links of the variator in the kinematic chain between the transmission of the machine and the flywheel make it possible to maintain a constant total value of the kinetic energy of the transmission of the machine and the flywheel.

A control device for recovering energy from a machine is known, including a traction motor and transmission, interconnected by a gear transmission with a constant gear ratio with one degree of mobility, which also includes a reversible electric machine, a flywheel and a planetary differential with two degrees of mobility, consisting of two central gears ( of which one central gear with an internal tooth), and the other central gear with an external tooth is called the central stubble, as well as of the carrier and the satellite located on the carrier and engaged with two central gears, wherein the flywheel is connected to the central gear.

A machine energy recovery control device is proposed, characterized in that it is additionally equipped with a gear transmission connecting the central gear of the planetary differential with the flywheel, the transmission is connected to the central gear wheel, and the carrier is connected to the control electric machine. Such a combination of the planetary differential with the flywheel reduces the kinetic energy loss during braking by maintaining a constant value of the kinetic energy of the machine and flywheel transmission, which in turn is possible only when the current transmission speed of the machine is automatically measured, since the planetary differential forms a direct-acting mechanical regulator operating on the principle Poncelet [4].

The machine’s energy recovery control device, including a traction motor and transmission, interconnected by a gear transmission with a constant gear ratio with one degree of mobility, also including a control reversible electric machine, a flywheel and a planetary differential with two degrees of mobility, consisting of two central gears (from which one has a central gear wheel with an internal tooth), and another central gear wheel with an external tooth, called the central gear, as well as from a carrier and a satellite located on the carrier and meshed with two central gears, the flywheel being connected to the central gear, characterized in that it is additionally equipped with a gear transmission connecting the central gear of the planetary differential with the flywheel, the transmission is connected to the central gear , and the carrier is connected to the control electric machine.

A significant difference of the proposed device from the analogue is that it is equipped with an additional gear transmission connecting the central gear of the planetary differential with the flywheel, the transmission is connected to the central gear wheel, and the carrier is connected to the control electric machine.

An additional difference between the proposed device and the analogue is that it is equipped with an additionally controlled clutch, with which the flywheel is connected to the central gear of the planetary differential, which, when turned off, allows the flywheel to rotate when the machine and the traction motor are stopped.

The best version of the device is characterized in that the proposed device from the analogue consists in the fact that it is equipped with two additional gears connecting the carrier with a control reversible electric machine and a transmission with a central gear wheel.

Thus, the proposed device differs from the analogue in that it is equipped with an additionally controlled clutch, by means of which the flywheel is connected to the central gear of the planetary differential, which, when turned off, allows the flywheel to rotate when the machine and the traction motor are stopped and is additionally equipped with two gears connecting the carrier to the control reversible electric machine and transmission with a central gear wheel.

The main set of essential features of the claimed device, which makes it possible to achieve the claimed technical result, is that the energy recovery control device of the machine is additionally equipped with a gear transmission connecting the central gear of the planetary differential with the flywheel, the transmission is connected to the central gear wheel, and the carrier is connected to the control an electric machine that is equipped with an additionally controlled clutch, with which the flywheel is connected to the prices tral planetary gear differential which provides at shutdown rotatable flywheel when the machine is stopped and the traction motor, and in that further provided with two toothed gears connecting the carrier with the control of the reversible electric machine and the transmission with the sun gear.

The connection of the planetary differential links is made in various ways with the known and proposed devices. The connection of the links in the known device reduces the efficiency of energy recovery control and does not allow to provide a constant total value of the kinetic energy of the flywheel and the machine, since there is a simultaneous increase in the kinetic energy of all the links of the differential, flywheel and transmission during acceleration and a simultaneous decrease in their kinetic energy during braking.

A comparison of the properties of the claimed and known solutions shows that the proposed solution has new properties that do not match the properties of the known solutions, and that the claimed solution has significant differences.

BRIEF DESCRIPTION OF THE DRAWINGS

The invention is illustrated by drawings. Figure 1 shows the kinematic diagram of the proposed device for recovering braking energy of the machine: 1 - Central gear (gear with an external tooth); 2 - satellite (gear wheel with a moving axis of rotation); 3 - a central gear wheel (with an internal tooth); 4 - drove; 5 - planetary differential; 6 - traction motor; 7 - transmission; 8 - main gear; 9 - driving wheels; 10 - gear transmission (traction motor); 11 - gear transmission (flywheel); 12 - flywheel; 13 - control reversible electric machine; 14 - gear (control reversible electric machine); 15 - electric battery; 16 - electronic control device; 17 - gear transmission (transmission); 18 is a source of electrical energy.

The basis of the device is a planetary differential 5 with the number of degrees of freedom equal to 2, which includes well-known elements mechanically connected by kinematic pairs [3]: 1 - the central gear (a gear wheel with an external tooth); 2 - satellite; 3 - a central gear wheel (with an internal tooth); 4 - the carrier on which the satellite 2 is located. The central gear 1 is connected by a gear 11 with the fixed axles to the flywheel 12. The satellite 2 is located on the carrier 4 and engages with the central gear and the central gear; (with internal tooth). The carrier 4 is connected by a gear 14 with a control reversible electric machine 6. The central gear 3 is connected by a gear 17 with a transmission 7, which is connected to the main gear 8 with the drive wheels 9. The traction motor 6 is connected to the transmission by a gear 10.

The block diagram of the control device energy recovery of the machine shown in figure 2. The electronic control device 16 connects the electric accumulator 15, the control reversible electric machine 13, the traction motor 6 and the electric power source 18, which can be used as an electric generator driven by the internal combustion engine.

Changing the connections of the planetary differential of the claimed and known devices allows you to use the property of self-regulation, which was impossible when using the known device, which is a fundamental difference to increase the efficiency of the control system of the machine. This property of kinetic energy self-regulation follows from the analysis of velocity plans presented in Fig. 3.

WORK OF THE SUGGESTED DEVICE

Figure 3 shows the kinematic diagram of the planetary differential with the number of degrees of freedom equal to 2, and plans for the speeds of its links: 1 - the central gear; 2 - satellite; 3 - the central wheel (with an internal tooth); 4 - drove. The carrier 4 (connected in FIG. 1 with a reversible electric machine) rotates around a fixed center O ₁ . The center of rotation of the O ₂ satellite has a linear velocity V _O2 . At the contact points of P _{1 of} satellite 2 with the central gear 1 and P _{2 of the} central gear 3 (with internal tooth), their speeds V ₃ and V ₁ are equal to the speeds of the points of satellite 2. Linear speeds V ₃ and V ₁ determine the law of distribution of speeds and speed 2 satellite center V _O2 , associated with the rotation speed of carrier 4.

The change in speed V ₃ using the control reversible electric machine 13 associated with the electronic control device 16 (figure 2) causes a change in speed V ₁ and the rotation speed of the flywheel 12. A change in the speed of rotation of the transmission 7, determined by the speed of the machine, causes a change in speed V ₃ the Central gear 3 and the speed V _{1 of the} Central gear and the associated flywheel 12. Thus, the effects of speed V ₃ associated with the speed of the machine, and speed V _O2 drove 4, associated with the control my electric machine 13, causes a change in the speed of rotation of the Central gear 1 and the associated flywheel 12.

On the speed plan of Fig. 3, constructed in the coordinate system, the linear velocity V and the radius of the point, the angular velocities of the links are proportional to the tangent of the rays [3]. From the speed plan it follows that an increase in the speed of the machine and speed V ₃ during acceleration and a decrease in the speed V _O2 causes a decrease in the speed V ₁ and the speed of rotation of the flywheel 12. When braking the machine, the opposite phenomenon is observed - a decrease in the speed of the car and an increase in the speed V _O2 , which induce growth rate V ₁ and the speed of rotation of the flywheel 12. This interaction of the traction motor 6, which determines the speed of the machine, with the control of the reversible electric machine 13 leads to a self-leveling kinetic energy uu transmission 7 and a differential planetary units 5 connected to the flywheel 12.

Since the rotation speed of the carrier 4 is determined by the control reversible electric machine 13, associated with the electronic control device 16, the acceleration or deceleration of the machine is determined by changing the torque of the traction motor 6 and the control reversible electric machine 13. Maintaining a constant total value of the kinetic energy of the flywheel 12 and the transmission 7 of the machine is carried out due to the characteristic of the differential, in which a change in the speed of the machine causes a corresponding change ix flywheel rotation speed of 12.

, имеющими направление рекуперации механической энергии от ведущих колес 9 машины к маховику 12 и от тягового электродвигателя 6 к управляющей обратимой электрической машине 13. Тяговый электродвигатель 6 работает в режиме электрического генератора, управляющая обратимая электрическая машина 13 работает в режиме электродвигателя, избыток электрической энергии передается в аккумулятор. При торможении происходит подзарядка электрического аккумулятора 15 от тягового электродвигателя 6 и от источника электрической энергии 18.The direction of energy flow during braking is shown in Fig. 2 by arrows

having the direction of recovery of mechanical energy from the driving wheels 9 of the machine to the flywheel 12 and from the traction motor 6 to the control reversible electric machine 13. The traction electric motor 6 operates in the electric generator mode, the control reversible electric machine 13 operates in the electric motor mode, the excess electric energy is transmitted to battery. When braking, the electric battery 15 is recharged from the traction motor 6 and from the electric energy source 18.

, от аккумулятора 15 к тяговому электродвигателю 6 и к ведущим колесам 9 от маховика 12 и от тягового электродвигателя 6 к управляющей обратимой электрической машине 13. Управляющая обратимая электрическая машина 13 работает в режиме электрического генератора.During acceleration, the opposite effect is observed. The direction of the energy flow is reversed and is shown in figure 2 by arrows

, from the battery 15 to the traction motor 6 and to the driving wheels 9 from the flywheel 12 and from the traction motor 6 to the control reversible electric machine 13. The control reversible electric machine 13 operates in the mode of an electric generator.

In the steady-state mode of motion at a constant speed of the Machine, energy flows from the source of electric energy 18 and from the battery 15 to the traction motor 6 with the corresponding control signal from a reversible electric machine 13, which operates in the mode of an electric generator. In the absence of an electric energy source 16, the power to the traction motor 6 is supplied only from the battery 15, which must be periodically recharged from an external power source (not shown in the figures). By choosing the power of the electric energy source 18, which can be used both in steady-state mode of motion and during acceleration, it is possible to balance the battery operation without recharging from an external power source.

From the consideration of figure 3 it follows that the supply of kinetic energy of the flywheel 12 with a decrease in its speed is automatically transferred to the transmission 7 of the machine and leads to an increase in the speed of the machine during acceleration. And, conversely, the supply of kinetic energy of the flywheel 12 automatically increases with a decrease in the speed of the transmission 7 during braking of the machine. The operation of a controlled reversible electric machine 13 in the electric motor or electric generator mode, you can change the process of kinetic energy exchange between the flywheel 12 and the transmission 7 of the machine for acceleration or braking. The process of transferring energy from the flywheel 12 to the transmission 7 or in the opposite direction is automatically controlled by the self-leveling characteristics of the planetary differential 5 when the selected links of its links with the elements of the transmission 7 by adjusting the torque of the controlled reversible electric machine 10 with any change in the operating mode of the machine by maintaining a constant supply kinetic energy of the moving parts of the machine. A planetary differential 5 with two degrees of freedom W = 2 forms a direct-acting mechanical regulator operating according to the Poncelet principle [4].

Best device option

The control device starts to work after starting the traction motor 6 and the beginning of the movement of the machine, leading to an increase in the speed of the transmission 7. The flywheel can store energy after the first stop of the machine. It is necessary that when the machine and the traction motor 6 are stopped, the flywheel 12 does not stop and does not lose the kinetic energy accumulated during braking.

For this, the machine’s energy recovery control device is equipped with an additionally controlled clutch (not shown in the figures in view of its well-known design), by means of which the flywheel 12 is connected to the central gear 1 of the planetary differential 5. Forcing disengagement of the controlled clutch allows the flywheel to maintain maximum rotation speed when stopped transmission 7 and off control reversible electric machine 13.

INDUSTRIAL APPLICABILITY

The inventive method of controlling energy recovery of the machine and the device for its implementation can improve the efficiency of electric vehicles and reduce energy consumption compared with the known devices of transport vehicles. Energy losses of cars increase during braking and when they stop. Therefore, the use of the inventive method and device for recovering energy from a machine can reduce energy losses and increase the efficiency of cars in any unsteady operating conditions by changing the gear ratio between the transmission of the transport machine and the flywheel according to the proposed dependence, which provides complete recovery of braking energy without kinetic losses and safe operation.

Literature:

1. Gulia R.V. Inertia. - M.: Science, 1982. - 152 p.

2. Flywheel drive system (United States patent 4.23 3.85 8 Nov. 18. 1980 PCT / US 019778 WO 2008/033378 App. No. 754, 597 Dec.27, 1976 Int cl ³ F16h 37/06, B60K 1 / 00.

3. I.I. Artobolevsky. Theory of mechanisms and machines. M .: Science. 1975.640 s.

4. Krugov V.I. Automatic regulation of the engine.

Claims (5)

1. The method of controlling the energy recovery of the machine, which consists in changing the gear ratio of the variator U _var in the kinematic chain between the transmission of the machine and the flywheel, characterized in that a constant total value of the kinetic energy of the transmission of the machine and the flywheel is provided by changing the gear ratio of the variator U _var according to the relation that transmission rotation speed ω _tr and flywheel rotation speed ω _max
U _Var = {[(ω _{swings) max} / ω _tr] ² -1} ^1/2 2. The method according to claim 1, characterized in that the rotation speeds of the input and output links of the variator in the kinematic chain between the transmission of the machine and the flywheel have opposite directions. 3. The control device for energy recovery of the machine, including a traction motor and transmission, interconnected by a gear transmission with a constant gear ratio with one degree of mobility, which also includes a control reversible electric machine, a flywheel and a planetary differential with two degrees of mobility, consisting of two central gears (of which one central gear with an internal tooth and the other central gear with an external tooth is called the central gear j), as well as from the carrier and the satellite located on the carrier and meshed with two central gears, the flywheel being connected to the central gear, characterized in that it is additionally equipped with a gear transmission connecting the central gear of the planetary differential with the flywheel, the transmission is connected to the central gear wheel, and the carrier is connected to the control electric machine. 4. The device according to claim 3, characterized in that it is equipped with an additionally controlled clutch, by means of which the flywheel is connected to the central gear of the planetary differential, which, when turned off, allows the flywheel to rotate when the machine and the traction motor are stopped. 5. The device according to claim 4, characterized in that it is additionally equipped with two gears connecting the carrier with a control reversible electric machine and a transmission with a central gear.

Images