SU994652A1 - Hydrodynamic drive - Google Patents

Description

(54) HYDRODYNAMIC DRIVE

one

The invention relates to machines whose operation is characterized by transients, corresponding to the modes of acceleration and deceleration, rotating, and progressively moving their masses. Moreover, these modes of drying are driven by a hydrodynamic transmission activated by friction elements. The most common types of such machines are single-bucket excavators with a flexible suspension of working equipment and motor rollers with smooth rollers.

A hydrodynamic drive is known, which consists of a kinematically coupled engine, a torque converter, a friction reverse gearbox and mechanical transmissions to the actuators 1.

The disadvantage of the famous. The design is a significant work of slipping in the reverse-friction clutches.

A hydrodynamic drive of motorized road rollers is known, consisting of a kinematically coupled engine, a friction reversing gearbox, a torque converter with rotary vanes, a mechanical transmission and an actuator.

a mechanism (a running gear with which the leading rollers are connected), as well as a device, kinematically linking the friction reverse gear control mechanism with the blade rotation mechanism

5 torque converter 2.

The disadvantages of the known hydrodynamic drive are the complexity of the design and the significant work of slipping.

10 The purpose of the invention is to simplify the design and reduce the work of slipping in friction reverse gears.

1Del is achieved by the fact that the hydrodynamic transmission is made in the form of start-up hydraulic couplings with a split pump wheel 15, the parts of which are interconnected by a friction clutch, one of the parts being kinematically connected with the output shaft of the reverse-reducer. FIG. 1 is schematically depicted.

2Q is a proposed hydrodynamic drive in which the inner part of the impeller of the booster brake coupling is connected with the output shaft of the friction reversing gear unit; in fig. 2 is the same in which the outer part of the pumping wheel of the pus-braking 1-I-clutch is connected to the output of the friction reverse gearbox.

Hydrodynamic drive includes engine 1, friction clutch 2. friction reverse gear 3, start-up brake clutch 4, mechanical. for example, the gears of the undercarriage 5, which drive the rollers 6, the roller (or the gears to the pivot mechanism that drives the platform of the excavator).

The friction reverse gear consists of leading gears 7, friction clutches 8 and 9, driven shchestren 10 and the output shaft 11.

The starting and brake fluid coupling consists of a split impeller in the form of an inner H and outer Ng parts, a turbine wheel T, and a friction clutch 12 for connecting the inner and outer parts of the impeller.

The inner part of the pump wheel HI (Fig. I) or its outer part Hg (Fig. 2) is connected to the output shaft 11 of the reverse gearbox 3. The outer part of the pump wheel Hj (Fig. 1) or its inner part H, (Fig. 2) rotates freely on the bearings 13 and can be associated with the inner (or outer) part of the impeller by means of the clutch 12.

The turbine wheel of the hydraulic coupling T is connected with the drive shaft of the mechanical transmission part 5. A distribution system, for example, a spool device 14 with a control handle 15, is used in the drive system. In the spool device there are feed 16 and 17, as well as return lines 18 and 19 for liquid. The control handle 15 has 5 positions: neutral O, two positions 1c and 2c “forward and two positions 1n and 2k” back.

The operation of the hydrodynamic drive is carried out as follows.

With the engine running 1, the clutch 2 engaged and the handle 15 in neutral, the clutches 8 and 9 are turned off. Start-brake fluid coupling and transmission disconnected from the engine. By moving the handle 15 to the position, for example, 1c, the friction clutch 8 is turned on. The internal H, (or external H) part of the hydraulic clutch pumping wheel is rotated, and the fluid in it starts smooth acceleration of the turbine wheel T and the masses associated with him, due to the torque generated by the wheel Hj (or On). When the handle 15 is moved from position 1c to position 2e, the friction clutch 12 is engaged. It enters the operation simultaneously with the inner (outer), (outer) (inner) part of the impeller. In this case, a more intensive acceleration of masses is achieved due to the torques created by the inner HI and the outer Ng of the impeller parts together. In this way, the machine moves forward or the masses of the ascavator are moved left or right. When the handle 15 is switched to the 1n position, the friction clutches 12 and 8 are switched off and the friction clutch 9 is switched on. At the same time, first, the internal HI or external part of the impeller is reversed, and then the brakes are reversed and the masses are accelerated in the opposite direction. In this way, the machine is reversed.

In the proposed drive, masses can be accelerated and decelerated due to the torque generated by

the inner (Fig. 1) or outer (Fig. 2) part of the impeller or due to the torque generated by both parts of the impeller. Due to this, the torque is automatically limited, as during acceleration,

and in the process of inhibition of the masses, regardless of the subjective factors of the driver.

Due to the fact that the moment of inertia of the accelerated and reversible part of the impeller is significantly less than the moment of inertia of the mass of the roller or excavator, the slipping operation in clutches 8 and 9 is reduced compared with the slipping operation occurring in machines with widely used mechanical gears. as well as a hydrodynamic drive, in which the main torque converter is installed after the engine.

The application of the invention provides a simplified design by eliminating the rotary blades in

the torque converter and devices linking the mechanisms for controlling the friction clutches of the reverse gearbox and rotary blades, a deeper limit for adjusting the torque during acceleration

and braking of masses due to the characteristics of the start-brake hydraulic clutch and reduction of slipping operation in the clutches 8 and 9 during the reversal process due to the lower moment of inertia of the reversible mass of the part of the pump wheel of the start-brake hydraulic clutch compared to the moment of inertia of the pump wheel of the torque converter.

The cost of a torque converter with rotary blades together with devices kinematically linking the control mechanisms of the friction reversing gear and rotary blades of the torque converter, for example, for a roller weighing 10-13 tons is approximately 1000 rubles, and the cost of the proposed brake start brake coupling is 500 rubles. Provided the device has a service life of 5 years, only by reducing the cost of the drive, the economic effect of its use will be 100 rubles. per year per car.

Claims (1)

Invention Formula Hydrodynamic drive of rollers and flexible-mounted excavators of working equipment, including kinematically coupled engine, friction reversed reducer, mechanical transmission to actuators, hydrodynamic transmission, the pumping wheel of which is connected to the output shaft of the reverse-reducer, in order to simplify the design and reduce the work sliding gears in reverse gear reducer clutches, hydrodynamic transmission is made in the form of a start-brake fluid coupling with a split pump wheel, and which are interconnected clutch, wherein one part kinematically linked to the output shaft reverse gear. five Sources of information taken into account in the examination 1. Bratslavsky X. L. Hydrodynamic transmission of construction and road machines. M., “Mechanical Engineering, 1976 2 USSR Copyright Certificate No. 301295, cl. E 01 C 19/26, 1% 9 (prototype).