RU167619U1 - TWO SPEED FLYWHEEL FOR PIPELINE FITTINGS - Google Patents

Abstract

The proposed two-speed flywheel is a combination in a single structural design of a conventional flywheel with a two-speed drive of a large gear ratio (10-20) and efficiency, in the dimensions of the used flywheels and with the usual fit on the valve shaft, valve drive or other torque receiver. The flywheel contains an integral assembly 1 of a rim, spokes, possibly a handle and a housing, which is essentially a carrier of a two-wheeled planetary gear K-H-V of internal gearing. This assembly 1 rolls in the big wheel 2 along the small wheel 3, which is fixedly mounted on the axle in the end face of the hub housing 1. From the big wheel, the amplified moment is transmitted to the parallel shaft of the flywheel 4 and then to the shaft 6 of the torque receiver 5. A two-position stop is conventionally shown on the small wheel 3 - a speed switch 7, which connects the motionless small wheel 3 to the housing 5 of the output torque receiver in a lower gear or in direct gear, and connects the wheel 3 to the hub housing 1 (or directly to the shaft 6). K-H-V transmission can be embodied in gearing variants according to various exact (involute), approximate and piecewise-smooth curves, as well as in various variants of pinion gearing and gearing with intermediate bodies. Application of the flywheel to almost all types of pipe fittings makes control always two-speed and gives a significant reduction in the required manual force while reducing the opening / closing time. Moreover, the use of a flywheel in cases of direct control of valves or in combination with manual actuators, or as part of a manual understudy cardinally changes the current picture of types and models of actuating devices:

- The flywheel control range (without drive) will expand to 1000 Nm.

- At medium and heavy loads, combinations with single-speed drives compared to existing drives simultaneously reduce the required manual force and opening / closing time by 1.5-2 times.

- The ratio of the use of worm-spyroid and gears with less loss (conic, hypoid.) In favor of the latter.

- Application in a manual backup can significantly simplify the design of the drive and reduce the opening / closing time in an extreme situation.

The claimed device may be applicable in other cases of manual control of various technological processes, in particular in the flywheels of transport and agricultural machinery, in winches, steering wheels, etc.

Description

Technical field

The proposed technical solution relates to mechanical engineering, namely to valve engineering, more specifically to flywheels (F16K 31/60), and can be used as a single-speed flywheel-amplifier or as a two-speed flywheel with mode switching with amplification of the input moment in low gear to direct transmission without gain.

The device can be installed on:

- spindle or running nut of pipe fittings;

- the shaft of the manual valve drive;

- a shaft of a manual backup of a mechanized drive.

The flywheel is applicable to full-speed and part-turn, shut-off, adjustable and throttle valves with extendable and non-extendable spindles. Application is also possible in other cases of transferring manual force to the shaft of a driven device with a function of amplifying the input torque, for example, in winches or helms.

Terminology

The following concepts are used in the application materials:

“Receiver, driven device” - pipe fittings, manual drive of pipe fittings, manual backup drive of pipe fittings, another mechanism or device that is driven by a flywheel.

"Big wheel" - a larger-diameter wheel of a two-wheeled gear planetary gear of internal gearing type K-H-V.

"Small wheel" - a wheel of a smaller diameter of a two-wheeled gear planetary gear of internal gearing type K-H-V.

Note that under the prior art, the concept of planetary gearing of internal gearing of the K-H-V type includes gears with gearing proper along various curves (involute, Novikova, conchoid, approximate, etc.). The gear type with a pinion gear also along various cycloidal curves belongs to the same type. In this case, the sprocket wheel and the so-called asterisk can be both a large and a small wheel. K-H-V type planetary gears also include so-called planetary gears with intermediate bodies, in which the contact between the big and small wheels occurs through a ball or roller. In some cases, the adjective “wave” is completely unreasonably added to such transfers, since there is no specially deformable link in such a transfer. Thus, the application relates to any of the specified transmission options of one type K-H-V, the essence of which is the running of one wheel over another with the transmission of torque to a parallel shaft, but with the nuances of the clutch of this pair of wheels.

State of the art

Standards define the handwheel of pipe fittings as a wheel-shaped control in a single design, consisting of a rim, spokes and a hub. National regulations limit the rim diameter to 1 m, the cross section of the rim to 40 mm and the rim force to 450 N (global standard 360 N). Preferred values correspond to 0.4 m in diameter and 200 N in the applied force, which gives a preferred flywheel moment of 40 Nm. Turning the handwheel clockwise should correspond to the closing of the valve, and counterclockwise to the opening. To transmit torque, the flywheel is fixedly mounted on the receiver shaft and uses its supports. It is allowed to combine flywheels with other elements in a single design.

The standards limit the use of a flywheel without a drive to a load of 250 Nm, which, with a preferred diameter of a flywheel, requires a force of 625 N. Without additional tricks, an average person can hardly afford a long-term load of this size. It is known that for valves such as valves with a large difference in the magnitude of the moment in the open / close cycle, a two-speed mode is required. Otherwise, either the force or the opening / closing time of the valve will be excessive.

Thus, the relevance of creating a two-speed flywheel of pipeline valves with the possibility of amplifying the input moment in the low gear mode is quite obvious.

Known flywheels in a single design installed on the receiver shaft, in which, along with the direct function of transferring the manual force applied to the rim to the shaft, the tasks of the two-speed mode are solved. So, in patent RU 2416051 the flywheel is made double to control the switching of the drive stages. In patent RU 132855, a flywheel with the possibility of axial movement along the axis of the shaft serves a similar purpose. The disadvantage of such flywheels is the inability to strengthen the moment by the flywheel itself.

In patents CN 203477567 and RU 2022194, the flywheels can increase the input torque, however, in these solutions the flywheels are not made in a single design, do not “sit on the shaft”, but are inseparably connected with the structural elements of the valve or actuator. This dependence contradicts the accepted definition of a flywheel and the world classification of pipeline fittings.

In the prototype - patent SU 1196597 - the flywheel is made in a single design, is mounted on the receiver shaft, and its internal device provides the possibility of amplification of the torque. However, the use of the kinetic energy of goods sliding along the rim is inefficient and doubtful due to the possibility of sparking.

Task, technical result

The basis of this proposal is the task of combining the main function of the flywheel, as an organ of direct transmission of control from a person to a machine, with the additional function of reducing the moment, provided that the specified regulatory requirements are met and the standard concept of the flywheel is maintained in the form of a separate device with a mounting unit on the receiver shaft.

The technical result is the operation of the flywheel in the direct transmission mode without amplification of the input torque, as well as in the downshift mode with the amplification of the input torque, in other words, operation in the two-speed mode.

Brief Description of the Drawings

In FIG. 1 shows a kinematic diagram of the proposed flywheel design, which is a typical planetary gear type K-H-V placed on a small wheel placed in a flywheel hub.

In FIG. 2 (callout of Fig. 1) shows an example of a two-position controlled stopper for switching the operating modes of the flywheel, made in the form of a composite linearly movable pin in the sockets of the fixed links.

In FIG. 3 (callout of Fig. 1) shows an example of a two-position controlled stopper for switching the flywheel operating modes, made in the form of a rotary fist interacting with the grooves of the fixed links.

In FIG. 4 shows a similar view to FIG. 1 kinematic diagram of a flywheel using another mechanism for transmitting torque to a parallel shaft.

In FIG. 5 shows an example implementation of the kinematic diagram of FIG. four.

Disclosure, the essence of the proposal

The problem is solved in that:

a two-speed flywheel for pipe fittings, comprising a flywheel fitting assembly on the torque receiver shaft, i.e., on the pipe fittings shaft, on the pipe fittings drive shaft or on the manual backup shaft of the drive, comprising an integral assembly of a rim, spokes, hub housing, and possibly a handle, contains in the hub housing a planetary gear of the internal gearing of the KHV type with a fixed small wheel and a large wheel rolled around it, and the assembly of the rim, spokes, the hub housing and possibly the handle is a carrier m of this planetary gear;

one carrier knee, in the form of the lower end of the hub housing, is installed in the rotation support on the axle of the small wheel along its axis;

the other knee of the carrier, in the form of the upper end of the hub with a pin, serves as a support for the rotation of the large wheel installed in it along its axis;

in the center of the small wheel in the axle in the rotation support there is installed the flywheel output shaft, which is rigidly connected by the coupling to the shaft of the torque receiver;

any mechanism used to transfer torque to the parallel shaft in the K-H-V transmission transmits the moment from the hub of the big wheel to the flywheel output shaft in the downshift mode when the small wheel with the pin is motionlessly connected to the case of the torque receiver by a stopper, for example, a pin;

and in direct transmission mode, the small wheel is motionlessly connected by a stopper, for example, a pin, either to the hub housing or directly to the flywheel shaft, and then the entire flywheel traditionally rotates as a whole.

In the monograph [1] on page 11, fig. Figure 6 shows the kinematic diagrams of a two-wheeled planetary gear of internal gearing of the K-H-V type, which is described in detail in the book in the variants of involute and pinion gearing. The transmission contains an eccentric shaft, a fixed housing with a large wheel installed in it, a small wheel rolling around it with variants of the mechanism W for transmitting the amplified moment to the parallel shaft. However, the input and output shaft rotate in opposite directions, which contradicts the standards for valve control.

The book contains drawings of various designs of gears and gearboxes of this type in versions of gear involute and pinion gears. Shown, that

high efficiency at the level of a simple cylindrical gear and compact axial dimensions.

In FIG. 1 and callouts (Fig. 2 and Fig. 3) shows the kinematic diagram of the proposed two-stage flywheel in the input torque amplification mode, mounted on a fixed small wheel and, for example, with the W mechanism in the form of a double articulated coupling according to Fig. 6 from [1].

The flywheel contains an integral assembly 1 of the rim, spokes, hub housing. For accelerated rotation, the flywheel sometimes contains a conventional handle (the handle is not included in the formula and is not shown in the drawings). In the housing of the hub assembly 1, the links of the planetary gear of the internal gearing of the K-H-V type in the form of a fixed small wheel are installed. Assembly 1 is essentially the carrier of this gear. One knee drove 1 - the lower end of the hub housing - is installed in the rotation support on the axle of the small wheel 3 along its axis. Another parallel shifted knee carrier 1 - the upper end of the hub with a pin - serves as a support for the rotation of the large wheel 2 mounted on it along its axis. In the center of the small wheel in the axle in the support of rotation is installed the output shaft of the flywheel 4, which is rigidly connected to the shaft 6 of the torque receiver 5.

In the downshift mode, the amplified moment from the axle of the large wheel 2 to the output shaft 4 is transmitted using any applicable mechanism 8 for transmitting torque to the parallel shaft (see [1] on page 11, Fig. 6). In this mode, the immobility of the small wheel 3 with the pin is provided by the stopper 7, for example, in the form of a pin in the sockets of the pin of the small wheel 3 and the moment receiver 5 (the stopper in Fig. 1 is shown conditionally, in detail in Fig. 2 and Fig. 3).

In direct transmission mode, the small wheel 3 with the axle is fixedly connected by the stopper 7, for example, a cam (callout Fig. 3), with the groove of the hub housing 1.

In this case, the flywheel rotates as a unit with the shaft 4 on the shaft of the receiver of the moment 6, that is, the speed mode of direct transmission is traditionally ensured.

In a more complicated embodiment, not included in the formula, the small wheel 3 can also communicate directly with the shaft of the flywheel 4 (stopper not shown).

Device operation

The flywheel works as follows.

In the mode of amplification of the moment in low gear, the stopper 7 fixes the small wheel 3 relative to the housing of the receiver 5. When the carrier rotates behind the rim of the assembly 1

the second end of the carrier 1 runs a large wheel 2 along a fixed small wheel 3. The large wheel 2 slowly rotates about its own axis in the direction of rotation of the running-in. That is, with a fixed small wheel in the K-H-V gear, the input and output shafts rotate in the same direction. This slow rotation of the wheel 2 is transmitted by the mechanism 8 to the output shaft of the flywheel 4 and then to the shaft 6 of the torque receiver 5.

In the direct transmission mode without amplification of the moment, the stopper 7 fixes the wheel 3 relative to the assembly 1. Since the wheel 2 is always engaged with 3, the moment from the force on the rim is transmitted through the stopper to the wheel 2, then to the mechanism 8 and the output 4.

In the direct transmission mode, the stopper 7 can directly fix the shaft 4. The result is the same. The choice of fixation option is made for structural reasons. The first option is included in the formula as preferred.

Thus, in any case, the claimed technical result is achieved — the operation of the flywheel in the direct transmission mode without amplification of the input torque and in the mode of lower transmission with amplification of the input torque.

Proposal implementation, industrial applicability

The means, methods and designs for the industrial use of planetary gears of the K-H-V type according to the scheme of Fig. 6 from [1] with different types of gears: involute gears, pinion gears and gears with intermediate bodies (see [1], [2]). Therefore, the possibility of industrial use of such gears in the flywheel according to the scheme of FIG. 1 with identical worked out main structural units is quite obvious.

In FIG. 4 shows a similar view to FIG. 1 is a kinematic diagram, but in the variant of torque transfer using a parallel crank mechanism, as well as using hollow shafts 4 and 6 and central holes in 1 and 2 to pass the retractable spindle of the valve.

In FIG. 5 shows an example implementation of the proposal for the kinematic diagram of FIG. 4 and with the use of sliding bearings in the rotation bearings. The stop 7 in the direct transmission mode is shown conditionally.

Designation of positions, operation of the device and the technical result of FIG. 4 and FIG. 5 are completely similar to those of FIG. one.

Estimated in dimensions of the preferred size of the flywheel, transmission at an output moment of up to about 1000 Nm is arranged. In this moment range at an affordable cost, the proposed flywheel can replace the corresponding manual drives with conventional flywheels, as well as part of the conventional flywheels to reduce manual effort and at the same time the opening / closing time of the valve.

For loads of more than 1000 Nm, a combination of a two-speed flywheel with single-speed drives is very effective, turning the drive into a two-speed one.

So for a gear ratio of 240, the efficiency of a worm or spiroid single-stage transmission is less than 0.25, and that of a two-stage worm-worm is 0.49 (see [3], pp. 24-30). When using a flywheel with a gear ratio of 15.5 and a worm or spyroid gear with a gear ratio of 15.5, the total transmission efficiency will increase from 0.25 to 0.68 × 0.92 = 0.63. This is almost 2 times more than the efficiency of a single-stage drive, and almost 1.5 times more than the efficiency of the best two-stage drive. It is also extremely important that in direct transmission of the flywheel, the opening / closing time of the valve is also significantly reduced. It can be seen from the example shown that the requirements for a single-speed drive change sharply: the gear ratio decreases 10-20 times, but with the same load capacity. In a large range of moments, it is possible to replace gears with large losses (spiroid, worm) with gears with high efficiency.

Options, dependent items

In the application according to claim 2, it is proposed to use sliding bearings as bearings of the bearings of rotation (see Fig. 5). This, along with the achievement of the main technical result according to claim 1, makes it possible to reduce the dimensions and increase the corrosion resistance.

In the application according to claim 3, it is proposed for the fittings with a sliding spindle that the flywheel shaft is hollow, and in the upper end of the hub body, in the small wheel and in the mechanism for transmitting torque to the parallel shaft, central holes are made (see Fig. 5). The main technical result on the alternative points is obviously the same. An additional technical result is the possibility of skipping the spindle.

Regarding the type of engagement. In the application according to claim 4, it is proposed to use a gear with a predominantly toothed gear as a gearing of a K-H-V planetary gear, which, as you know, can have various shapes of a gearing contour (involutes, conchoids, approximate curves, piecewise smooth, etc.). An additional technical result of gearing consists in lesser required manufacturing accuracy.

It is possible to use a K-H-V gearbox with a pinion gear [1] or a K-H-V gearbox with a gear with intermediate bodies [4]. These options also obviously lead to the achievement of the main technical result, however, they are not included in the utility model formula. An additional technical result of the pin gearing consists in increased load capacity. An additional technical result of transmission with intermediate bodies is increased compactness.

In the application according to claim 5, it is proposed to use a two-position switchable stopper 7 with a handle. In callout A of FIG. 2, in the low gear mode, a design variant of the on-off shifted stopper with axial linear movement of the double pin 7 in the corresponding sockets of the lockable small wheel 3 with the receiver housing 5 and the hub housing 1 is shown. When the pin 7 is moved upward, the double pin 7 exits the socket of the housing 5 and enters hub housing socket 1. The flywheel is thereby switched to direct transmission. An additional technical result consists in the simplification and convenience of switching.

In callout A in the embodiment of FIG. 3 also in the downshift state, a design variant of the on-off switchable stopper 7 with the rotation of the radially located cam 7 along the axis on the pin of the small wheel 3, interacting with the grooves of the hub housing 1 and the receiver housing 5 is shown. When the cam 7 is rotated, it also breaks the connection of the small wheel 3 with the housing of the receiver 5, but is engaged with the housing of the hub 1 and includes a direct transmission (shown by a dotted line). An additional technical result consists in the simplification and convenience of switching. The main technical result is the same.

Information sources

1. V.N. Kudryavtsev, “Planetary gears,” M., Mechanical Engineering, 307 pp., 1966

2. A.E. Belyaev, “Mechanical Transmissions with Intermediate Bodies”, Tomsk, TPI, 1986

3. V.I. Goldfarb et al., “Spiroid gearboxes for pipe fittings”, M., Veche, 222 pp., 2011

Claims (5)

1. A two-speed flywheel for pipe fittings, comprising a knot for mounting the flywheel on the shaft of a torque receiver, comprising an integral assembly of a rim, spokes, hub housing, characterized in that this assembly is a carrier of a planetary gearbox of internal gearing type KHV with fixed small a wheel and with a large wheel rolled around it; one carrier knee, in the form of the lower end of the hub housing, is installed in the rotation support on the axle of the small wheel along its axis; the other knee of the carrier, in the form of the upper end of the hub with a pin, serves as a support for the rotation of the large wheel installed in it along its axis; in the center of the small wheel in the axle in the rotation support there is installed the flywheel output shaft, which is rigidly connected by the coupling to the shaft of the torque receiver; the mechanism for transmitting torque to a parallel shaft used in K-H-V transmission transmits the moment from the axle of the large wheel to the flywheel output shaft in the reduction gear mode, when the small wheel with the axle is motionlessly connected to the housing of the torque receiver by a stopper; and in direct transmission mode, the small wheel is motionlessly connected by a stopper to the hub housing, and then the entire flywheel traditionally rotates as a unit. 2. A two-speed flywheel according to claim 1, characterized in that the bearings of rotation are installed bearings. 3. A two-speed flywheel according to claim 1 or 2, characterized in that for the passage of the retractable spindle of the valve, the flywheel shaft is hollow, and central holes are made in the upper end of the hub body, in the small wheel and in the moment transmission mechanism between the parallel shafts. 4. A two-speed flywheel according to claim 1 or 2, characterized in that gearing is used as the gearing of the pair of large and small wheels. 5. Two-speed flywheel according to claim 1 or 2, characterized in that the stopper is operated by a switchable on-off.

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