RU2483216C1 - Semigear-and-rack piston machine - Google Patents

Abstract

FIELD: machine building.

SUBSTANCE: piston machine includes a casing with cylinders fixed in it; pistons are connected via two-sided gear racks, each gear rack via shafts with semigears and a number of gears is connected to a root shaft (shafts).

EFFECT: enlarging capabilities of the piston machine; the machine is reversible because it can be used as a high-efficiency internal combustion engine, as well as a compressor or a pump, including a multicylinder one, besides, alignment of piston machines with different dimensions and various purpose is possible: quick-speed internal combustion engine with small dimensions with low-speed internal combustion engine (ICE) with large dimensions, ICE and a compressor, and ICE and a pump.

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Description

The proposed device relates to mechanical engineering, in particular to engine building, the production of compressors, pumps.

Piston machines are used as internal combustion engines, compressors or pumps.

A device is known - ICE (internal combustion engine), the basis of which is KShM (crank mechanism), which converts the reciprocating motion of the piston into rotational motion of the crankshaft (1. Internal combustion engines: Design and operation of piston and combined engines / V. P. Alekseev et al. - M.: Mechanical Engineering, 1990. - 288 p.).

However, the crankshaft has significant drawbacks: the force from the gas pressure on the piston is not fully used to rotate the crankshaft, reducing the efficiency of the mechanism and the engine, “rearrangement” of the piston occurs at dead points — a change in the direction of the lateral force, which creates dynamic loads. KShM is structurally complex - it has several loaded swivel joints: main and connecting rod necks, piston pin bearings, requiring a perfect lubrication system with supply of motor oil under pressure. To balance the mass of cranks, it is necessary to install balances, you need a flywheel that accumulates the energy of the working stroke, providing other engine strokes, as well as the passage of the piston through the dead points.

The force from the gas pressure on the piston is decomposed into two components: one along the axis of the connecting rod, the other creates a lateral load on the piston, causing energy loss due to friction and wear. The force acting along the connecting rod axis on the crank pin also decomposes into two components: one loads the main necks, and the payload - the torque on the crankshaft creates only the second component of the force perpendicular to the crank.

Known rodless internal combustion engines without crankshaft on the basis of copyright certificate No. 118471 (2. Balandin S.S. Rodless piston internal combustion engines. - M .: Mechanical Engineering, 1972. - 176 p.). The rod-free mechanism makes it possible to constructively carry out a two-sided working process in cylinders with small dimensions and high speed of engines and, as a result, obtain almost twice the liter and overall power / 2 /.

However, the rodless mechanism has complex kinematics (/ 2 / see Fig. 3-10 and others). In a number of designs, the function of the connecting rods is performed by the sliders, but in any case there remains a crankshaft, which is difficult to manufacture, its main necks need lubrication under pressure, gears must be installed between the crankshaft and drive shafts (/ 2 / see Fig. 12), which complicate engine design.

Known rack gears interconnected with pistons. The world’s first steam three-wheeled wagon, Kunho, was driven to the front wheel by two pistons of steam engines with racks working alternately. One of N. Otto’s first engines had a vertical cylinder, the piston of which interacted with the rack and pinion of the power take-off shaft through an overrunning clutch.

However, these machines and mechanisms were imperfect, had a low efficiency, low rotational speed, and hence low power. Freewheels are short-lived, they do not provide a clear response at high speed.

Closest to the proposed technical solution is a piston machine with a gear-rack mechanism (1. p. 262, fig. 182, b).

It is known that such a piston machine consists of cylinders located in them oppositely deployed pistons with a gear rack pivotally mounted on each piston engaged with a gear fixed to the shaft.

However, a piston machine with such a mechanism has limited capabilities and the gear-rack mechanism is used only as a synchronizing mechanism on high-speed gas generators.

The problem to which the claimed technical solution is directed is to expand the capabilities of a piston machine with a gear-rack mechanism.

The essence of the proposed device is that:

1) a half-gear rack piston machine contains a crankcase with cylinders fixed in it, pistons with gear racks, while the pistons are connected by two-sided gear racks, each gear rack is interconnected with half gears fixed on the shafts, which can be radical, matching ones are installed on the ends of the shafts gears engaged through an intermediate gear located on an axis fixed to the crankcase, this gear can be combined with the main shaft, there can be several main shafts.

2) a half-rack and pinion piston machine according to claim 1, wherein the adjacent cylinder shafts of different dimensions are interlocked with a synchronizing gear or gears.

The proposed technical solution significantly expands the capabilities of the piston machine, it is reversible - it can be used as a high-speed high-speed ICE, as well as a compressor or pump, including a multi-cylinder, in addition, it is possible to combine piston machines of different sizes and for various purposes - a high-speed ICE of small dimension with low-speed ICE of large dimension, ICE and compressor, ICE and pump.

Figure 1 shows a simplified diagram of a half-rack and pinion piston machine with a double-sided gear rack of a constant profile in a state when the pistons are in the extreme left position: the left piston at TDC (top dead center), the right piston at BDC (bottom dead center). For a piston machine with a horizontal arrangement of cylinders TDC and BDC are absent - they are located on the same level. It is advisable to name these points: VCT - the far extreme point and BKT - the near extreme point in relation to the center of the piston machine. The diagram does not show the gas distribution mechanism, cooling system, lubrication, etc.

Figure 2 shows a simplified diagram of a half-rack and pinion piston machine with a double-sided gear rack of variable profile in the state when the pistons are in the extreme left position.

Figure 3 shows a cross section of a half gear rack piston machine along the axes of the arrangement of the half gears. The section is simplified - seals, fixing bearings, axles, etc. are not shown.

Figure 4 shows the simplified kinematic diagrams of a half-gear rack piston machine along the axes of the location of the half gears: view "a" corresponds to figure 3, view "b" - the layout of the piston machines of different speeds when the cylinders are arranged in two rows - "in layers."

Figure 5 presents a simplified kinematic diagram of a half-gear rack piston machine along the axes of the location of the half gears - a layout diagram of the piston machines of different speed when the cylinders are in the same plane. View "a" is a transverse section, view "b" is a fragment of a longitudinal section at the level of bilateral gear racks.

In the crankcase 1, cylinders 2 with cylinder heads 3 are fixed. In the cylinders 2, pistons 4 are installed with compression and oil scraper piston rings connected by double-sided gear racks 5. The rails 5 are engaged with the half gears 6 fixed on the shafts 7. On the ends of the shafts 7 matching gears 8 are installed interlocked through an intermediate gear 9 located on an axis 10 fixed in the crankcase 1. It is possible to manufacture the intermediate gear 9 together with the main shaft 11 installed in the bearings of the crankcase 1. Any of the shafts 7 can perform the functions of the main shaft 11, while the main shaft 11 may be several.

The synchronizing gear 12 (see figure 4, 6 and figure 5) is engaged with the matching gears 8 of the shafts 7 of the piston machines of different sizes. The numbers with one stroke at the top (8 ', etc.) belong to a small-sized piston high-speed car, the numbers with two strokes belong to a large-sized piston low-speed machine.

The proposed half-gear rack piston machine operates as follows.

1. ICE mode. In figures 1 and 2, the left stroke is the force from the gas pressure of the burning working mixture in the left part of the cylinder 2 acts on the left piston 4 and the lower gear of the double-sided gear rack 5, the teeth of which interact with the teeth of the lower half gear 6, forcing it and the lower shaft 7 (see FIG. 3) rotate clockwise. From the lower shaft 7 of the gear 8, the matching gear 9, the force is transmitted to the gear 8 of the upper shaft 7 and the half-gears fixed on it 6. At this time, the upper half-gear 6 rotates idle also clockwise, since there are no teeth on its right section. Torque from the lower half-gear 6 through the lower shaft 7 is supplied to the main shaft 11. The main shaft 11 transfers energy to the flywheel (not shown in the diagram), which provides the drive for actuating and auxiliary mechanisms, and also accumulates part of the energy for other engine cycles. If the engine is four-stroke, then in the right cavity of cylinder 2 there can occur either an exhaust cycle - exhaust gas displacement, or an air compression cycle (diesel engines or gasoline engines with direct fuel injection) or a compression of the working mixture (carbureted or engines with centralized or distributed fuel injection in the intake collector). When the right piston 4 reaches the VCT, the lower half gear 6 disengages from the lower gear of the double-sided gear rack 5, at this time the upper half gear 6 engages with the upper gear of the double-sided gear rack 5 and changes its direction of movement.

In figure 2, the half gears 6 have a variable radius R, and the longitudinal profile of the gears of the rack 5 is curved. Given a constant ω - angular velocity of the shafts 7 and half gears 6, we obtain a variable linear speed V of the double-sided gear rack 5 and pistons 4. V = ωR. In figure 1, R = const.

2. Compressor or pump mode. Applying a torque to the main shaft 11, matching gears 8, shafts 7 and half gears 6, we move the double-sided gear rack 5 and pistons 4. If the teeth of the lower half gear 6 mesh with the lower gear of the double-sided gear rack 5, then it moves the rack from the left position to the right (see figures 1 and 2). In the right half, for the compressor, air (gas) compression or for the pump liquid displacement, in the left half - air (gas) inlet (suction) or liquid filling. When the lower half gear 6 disengages from the rack 5, the upper half gear 6 engages, the force is transmitted to the upper row of teeth of the rack 5, which moves the pistons 4 from the right to the left. In the left half - air (gas) compression or liquid displacement, in the right half - air (gas) inlet (suction) or liquid filling.

A half-rack and pinion piston machine can be either single-cylinder (single-piston) or multi-cylinder. The layout of the machine allows the use of one cylinder for the installation of two opposed pistons. The use of multi-cylinder engines will make it possible to obtain high-power internal combustion engines, while a better balancing of engine operation will occur and a flywheel of lower relative mass will be required. Multi-cylinder multi-stage compressors with a sequential increase in gas pressure can be obtained not only due to the number of gears and the interconnected gear racks and pistons, but also by installing step pistons.

It is possible to use a multi-cylinder reciprocating machine with cylinders of different dimensions and speed. In figure 4, b, the cylinders of small dimension and high speed are located at the top, and the cylinders of large dimension of the slow-moving piston machine are located below. The lower shaft 7 ′ of the matching gear 8 ′ cooperates with the synchronizing gear 12 fixed on the upper shaft 7 ″. Shafts 7 'and 7' 'can interact through several gears 12.

In the longitudinal arrangement of a multi-cylinder reciprocating machine with cylinders of different dimensions and speed, the double-sided gear rack 5 'of the high-speed part alternately interacts with half gears 6', which have shafts 7 'and matching gears 8' ', synchronizing gears 12 (see Fig. 5, and gear engagement 8 'and 12 is shown conditionally) the torque is transmitted to the shafts 7' ', then to the half-gears 6' 'and the double-sided gear rack 5' 'of the slow-moving part of the piston machine.

It is possible to assemble ICEs of different speed, ICE and compressor, ICE and pump. For an internal combustion engine, it is advisable to use a gear transmission with shafts of approximately 2 between the shafts 7 'and 7' '. For example, the nominal speed of the high-speed part of the internal combustion engine is 4000 rpm, and the low-speed part is 2000 rpm (Figure 4, b gear ratio approximately 1.5). With this arrangement of the internal combustion engine, the high-speed part can be used as a starting engine (a disconnect clutch is not shown), as well as an additional source of power under severe operating conditions - heavy loads.

Claims (2)

1. Half-gear rack piston machine, comprising a crankcase with cylinders fixed in it, pistons with gear racks, characterized in that the pistons are connected by double-sided gear racks, each gear rack is interconnected with half gears fixed on shafts, which can be radical, at the ends matching shafts are mounted on the shafts, engaged through an intermediate gear located on an axis fixed to the crankcase. 2. The half-rack and pinion piston machine according to claim 1, characterized in that the adjacent cylinder shafts of different dimensions are interlocked with a synchronizing gear or gears.

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