RU1775008C - Engine-pump unit - Google Patents

Abstract

Usage: transport, road construction and tractor equipment. The inventive engine-pump assembly comprises a housing in which pistons are installed in the engine cylinders with the formation of combustion chambers, which are kinematically directly connected to the displacers parallel to the axis of the engine pistons and installed in the pump cylinder blocks by means of a rod and a traverse. pump chambers connected through a switchgear to hydraulic power lines. Motor cylinders and pump cylinder blocks are arranged parallel to the central axis of the unit in a circle centered on the central axis and with a uniform pitch, the number of cylinders and blocks is odd and not less than three. These cylinders are oriented in one direction by the combustion chambers and are provided with a common annular head 11 in which fuel supply equipment is located. The unit is equipped with switching hydraulic plates, on one of which pump cylinder blocks are placed around the circumference. The switchgear is made in the form of a rotating spool with a axis of rotation coinciding with the central axis of the unit, and counter surfaces on switching hydraulic plates with distribution windows in the hydraulic plate in communication with pump chambers and power hydraulic lines. The synchronization mechanism is made in the form of a swinging washer kinematically connected11 with the piston rods of the engine and a non-strong shaft. The gas distribution mechanism, the starting device and auxiliary devices are kinematically connected with a non-force shaft, 10 zpp-ft. 13 ill. ≫ & ^^ > & .AXI

Description

The invention relates to engines of pumping units and can be widely used in transport, road construction, tractor engineering and other industries as a power unit for driving hydroficated travel systems, working and auxiliary equipment of machines and stationary installations.

At the same time, the conversion of the fuel combustion energy in the engine into hydraulic energy at the pump outlet is carried out by direct transmission of the rectilinear motion and force of the engine piston to the pump plunger. In this case, intermediate transformations are excluded; knowledge of movement (in the crank mechanism of the engine, the mechanism of the inclined washer, pump, etc.), as well as the mechanisms themselves

motion conversion. This simplifies the design, reduces energy loss, significantly reduces the size and weight. However, the supply of the pump unit with this is very uneven, which imposes restrictions on its movement in the hydraulic systems of machines, and requires the use of special dampers. In addition, the absence of fixation of the upper and lower dead points of movement of the engine pistons leads to a variable value of the compression ratio of the combustible mixture, instability of the combustion process, and a drop in its efficiency, which makes it difficult to adjust the engine. The engine is started from complex spring or pneumatic devices, which is also a disadvantage.

A well-known engine is a pump assembly, comprising a housing with cylinders and pistons of an internal combustion engine arranged around a circle with a uniform angular pitch parallel to the central axis, pump cylinder blocks with hydraulic pump displacers located in them, directly connected to the engine pistons and forming pump chambers connected to the power main via a switchgear, synchronization mechanism of the movement: piston kennel, made in the form of a swash plate, kinematically connected with currents of the engine pistons, and a non-power shaft placed in the housing along the central axis on the bearing assemblies, as well as a gas distribution mechanism with intake and exhaust systems, a starting device, fuel supply equipment and auxiliary devices equipped with a drive from a non-power shaft.

A disadvantage of the known device is its large axial dimensions.

The aim of the invention is to stabilize the movement of the pistons, to order the combustion of the combustible mixture, to reduce the pulsation of the hydraulic pump supply, to facilitate the starting and driving of auxiliary devices, as well as to reduce axial haEarites.

For this, the engine-pump unit is equipped with switching hydraulic plates located in the base of the housing, pump cylinder blocks and engine cylinders are connected to the hydraulic plates, connected to each other, the engine cylinders are equipped with a common annular head and form combustion chambers oriented to one side, the number of cylinders selected odd, no less than that, fuel supply equipment is located in the annular head, the switchgear is made in the form of a rotating spool mounted on a carrier SG shaft and on the mating surfaces with distributive switching gidroplitah windows communicating with the pump and with power gidromagistral mi. In addition, in the unit, the gas distribution mechanism can be made in the form of valves placed in a common annular head. The exhaust system of the gas distribution mechanism can be spool, and the inlet valve. The intake system of the gas distribution mechanism can be spool, and the exhaust valve. The valve timing mechanism may be in the form of a cam.

The cam can be made face or radial. The rotating spool of the switchgear may be cylindrical or end-face. Hydraulic pump displacers can be located around a circle around piston rods. The fuel supply apparatus can be equipped with a high pressure fuel pump with an annular body and radially arranged plungers, and the drive mechanism of the fuel pump plungers can be made in the form of a radial cam mounted on a non-force shaft.

In FIG. 1 shows an engine - a pumping unit, a section through a plane passing through the central axis; in FIG. 2, section AA in FIG. 1 (joint of the cylinder head and the housing (crankcase) of the engine); in FIG. 3 is a section BB in FIG. 1; in FIG. 4 is a section BB of FIG. 1 (connector of the upper switching hydraulic plate and rotating spool, view of the mirror of the upper switching hydraulic plate); in FIG. 5- section G-G in FIG. 1 (connector of the upper switching hydraulic plate and rotating spool, view of the spool mirror); in FIG. 6 is a section DD in FIG. 1 (connector of a rotating spool and lower switching hydraulic plate, view of a spool mirror); in FIG. 7 is a section EE in FIG. 1 (connector of a rotating spool and lower switching hydraulic plate, view of the mirror of the hydraulic plate); in FIG. 8 - section FJ in FIG. 1 (high pressure fuel pump); in FIG. 9 is a section 3-3 in FIG. 8 (high pressure fuel pump); on fig, 10 - section II in fig. 1 (synchronization mechanism); in FIG. 11 is a fragment of a design with a rotating cylindrical zoo of a switchgear; in FIG. 12 is an embodiment of a valve timing mechanism; in FIG. 13 - a variant of the design of the unit with slotted gas distribution. The engine - pump unit comprises a housing 1, in which, with the formation of combustion chambers 2, pistons of the internal combustion engine are installed in engine cylinders 3, Pistons 4 are directly kinematically by means of rod 5 and crosshead 6 connected to displacers 7 (plungers, pistons) of the hydraulic pump; parallel to the axis of the pistons 4 of the engine and installed in the blocks 8 of the pump cylinders with the formation of the pump chambers 9, connected through a switchgear to the power hydraulic lines x 10 and 11. The unit has a starting device for example, made in the form of an electric starter (not shown, fuel supply equipment made, for example, in the form of nozzles 12, a high-pressure fuel pump 13 and a fuel supply pump (not shown). This embodiment of the fuel supply equipment takes place in the case of a diesel engine. in the case of using a forced ignition engine, the fuel supply apparatus is in the form of a carburetor or a forced injection system (not shown). The cylinders 3 of the engine and the coaxial blocks of 8 pump cylinders are arranged parallel to the central axis and with uniform angular pitch (axial diagram), the number of cylinders 3 of the engine and blocks of 6 pump cylinders is odd and at least three (in the given embodiment, five cylinders). The cylinders 3 of the engine are oriented with combustion chambers in one direction and are equipped with a common annular head 14 in which fuel supply equipment is located (nozzles 12). The unit is equipped with switching hydraulic plates 15 and 16, on one of which (hydraulic plate 15) blocks of 8 pump cylinders are placed around the circles. The switchgear is made in the form of a rotating spool 17 with the axis of rotation coinciding with the central axis of the unit, and the counter surfaces 18 and 19 on the switching plates 15 and 16, respectively, with the distribution windows 20 in the hydraulic plate 15, in communication with the pump chambers 9, the distribution windows 21 in the hydraulic plate 1 b, connected with power hydraulic lines 10 and 11 and with a suction hydraulic line 22 (in the case of a non-reversible pump section, designed, for example, to power the working equipment of mobile machines). The pistons 4 of the engine are interconnected kinematically by a synchronization mechanism made in the form of a swash plate 23 kinematically connected to the rods 5 of the pistons 4 of the engine. The unit is equipped with a non-force shaft 24 mounted in the housing 1 coaxially to the central axis on the bearing assemblies 25 and kinematically connected with the swinging washer 23. Rotating valve 17, the timing gear drive, made, for example, in the form of a cam 26, pusher 27, rocker arm 28, drive timing valves 29, a starter (starter), an electric generator and other auxiliary devices are kinematically connected to the shaft 24. A flywheel 30 is installed on the shaft 24, which may have a gear ring 31 for driving yes auxiliary mechanisms and is connected to the starter. The kinematic connection of the shaft 24 with the swinging washer 23 can be made in the form of an angular crank 32, perpendicular to the plane of the washer 23. The washer 23 is mounted on the crank 32 on the bearing assembly 33. With the rods 5, the washer 23 can be kinematically connected by means of a heel 34 mounted on the spherical shaft 35 of the rod 5. Each heel 34 is installed in the annular bore 36 of the washer 23 and is pressed against the ring on top of: masonry 37, having radial grooves 38 for passage of the shanks 35 of the rods 5. To prevent rotation of the washer 23, it v overlay 37 have radial groove 39, in to tory includes a rib 40 formed in the glass 41 synchronization mechanism. 6, the lower central part of the cup 41 has a spherical support 42 with hydrostatic discharge grooves 43. The rotating spool 17 of the switchgear has sickle-shaped distribution windows 44 on the side of the hydraulic plate 15 and the annular distribution windows 45 on the side of the hydraulic plate 16. The cylinders 3 of the engine are formed by wet sleeves 46, pressed into the housing 1 to form a cooler jacket 47 to circulate the cooling medium . The pistons 4 of the engine have compression rings 48 and oil rings 40. The rods 5 are fixed in the pistons x 4 with the help of piston pins 50. The traverses 6 are fixed on the rods 5 with the lock rings 51. For self-installation on the traverse 6 displacers 7 (plungers) of their mushroom hydraulic pump the heads are mounted in the radial grooves 52 of the yoke 6 with the possibility of swimming. Propellants 7

the hydraulic pump is equipped with seals 53, and in the blocks 8 of the pump cylinders drainage grooves 54 are made, communicated by the drainage channels 55 to the cavity of the cup 41. Lastly, they are connected to the drainage of the hydraulic system with the tank 56, The rods 5 have sealing assemblies 57 and guide sleeves 58 installed in blocks of 8 pump cylinders. All unit systems located on the head 14 are covered by a casing 59 in which a seal 60 is made for the distance sleeve 61 mounted on the shaft 24. Another distance sleeve 62 is installed between the cam gear 26 and the cam 63 of the high pressure fuel pump 13.

The unit has a discrete volumetric flow control system made in the form of hydrodistributors 6-1 and 65, connected by inputs with switching hydraulic lines 66 with distribution windows 21 and outputs with power hydraulic lines 10 and 11 and a suction hydraulic pipe 22.

FIG. 1 shows an embodiment of a gas distribution mechanism at least partially valve with valves 29 in a common annular head 14,,

In another embodiment (see, Fig. 13), the valve timing can be implemented at least partially by spool, e.g., slotted. In this case, the piston 4 is the spool itself, and gas distribution windows are made in the walls of the sleeve 46 — the inlet window 67 and the outlet window 68, in communication with the intake manifold 69 and the exhaust manifold

70 ,:

If the valve timing mechanism is implemented, the valve actuator 29 can be made in the form of a cam 26 end-face (Fig. 1) or radial (Fig. 12). Cam 26 can interact with rocker 28 through a bearing assembly

71, the valve 29 has a spring 72 and an oil seal 73,

The rotating spool 17 of the switchgear may be made (end-face (Fig. 1) or cylindrical (Fig. 11),

The plungers 7 of the hydraulic pump can be arranged in a circle around the rods 5, The drawings show an embodiment of an aggregate with 4 plungers 7 of different diameters located around a circle around each rod 5, Three plungers 7 are made, for example, with diameters related to each other, as di: d2: d3 1: 3. When

This area of these plungers 7 includes FI: Р2: РЗ 1: 3: 9, These plungers are located in pump chambers 9, which are connected to the hydraulic power line via a switchgear formed by hydraulic plates 15 and 16 and spool 17, switching hydraulic lines 66 and hydraulic distributors 64 m 11

The hydraulic pump has a recharge system with

a make-up pump (not shown), which can also be driven by a non-power shaft 24,

The unit works as follows,

The control valves 64 are mounted in a neutral position in which all flows from the hydraulic pump are looped back. After that, the shaft 24 is unwound from the starter, which drives the pistons 4 through the washer 23 and the engine is started,.

In chambers 2, burn the engine in accordance with it. when the pistons 4 move upwards, the compression of fresh air (or charge) occurs, injection of fuel near the top dead center (TDC) of fuel from injectors 12 for a diesel cycle (or ignition of the mixture in a carburetor engine), ignition of the fuel mixture in chamber 2

The increase in pressure that is transmitted to the pistons 4 of the engine and drives them down to the bottom dead center point. During the movement of the pistons 4 of the engine down, they directly transmit the movement of the displacer 7 (plungers) of the hydraulic pump through the crosshead 6. The movement of the pistons 4 of the engine and the associated displacers 7 of the hydraulic pump is carried out as under the action of the energy of the compressed combustion products

in chambers 2, as well as under the inertia of the piston groups, which accumulates in the first phase of the piston 4 stroke of the engine down due to the excess pressure of the products of combustion on the piston 4 under hydraulic force from the displacers 7 of the hydraulic pumps. In this case, at the end of the stroke of the pistons 4 and displacers 7, their movement is carried out due to the accumulated inertial energy in the first phase of the movement and

less due to the pressure of the combustion products.

When the pistons 4 of the engine move down, they act through the rods 5 on the washer 23, providing it.

motion, and through the crank 32 the 1T drive rotates the shaft 24, the washer 23 at the same time during the precession drives up the pistons 4, which perform the preparatory cycle (purging the chambers 2 and the fresh charge), as well as displacers 7 which suck in the fluid pump chamber 9.

When the shaft 24 rotates, part of the energy from it (about 15-20%) is spent on driving auxiliary devices (a purge compressor, generator, fuel pump, oil pump, fan, etc.), as well as on spinning the flywheel 30, which stores this energy.

The balance of forces and energies in the unit is selected so that the average useful work (including work on the drive of auxiliary devices) does not exceed the effective work of the combustion products. This is ensured by the appropriate choice of the diameter of the displacers 7, their number per piston 4, the choice of the diameters of the piston 4, as well as the pressures in the hydraulic system, the selection of power to drive auxiliary units and the loss of power in the unit. Short-term disturbances in the balance of forces and energy are compensated by the energy accumulated in the flywheel 30.

During the stroke of the pistons 4 near the BDC, exhaust combustion products are released from the chambers 2 and filled with fresh charge. This is done by a gas distribution system (valves 29, windows 67 and 68). Fresh air is supplied to the chambers 2 by a purge compressor.

The engine is cooled by flowing coolant through a cooling jacket 47, the circulation of which is generated by a pump.

In general, the operation of the engine is identical to that of conventional two-stroke propulsors.

The spool 17 of the end or cork type is driven from the shaft 24. When the spool 17 is rotated, it is periodically connected by its distribution windows 44 to the distribution windows 20 connected to the pump chambers 9. The distribution channels 44 are each connected to their annular distribution window 45 with internal distribution channels 45 provided with a corresponding distribution window 21 connected to one from switching hydroplates 66. Thus, when the spool 17 rotates, it provides switching of all equally located pump chambers 9 located on the same diameter, decreasing in volume volume (when the displacers 7 move down for discharge), with the corresponding pressure line 66 through the corresponding distribution windows 20, 44, 45 and 21, as well as all pump chambers 9 equally located on the same diameter, increasing in volume (when the displacers 7 move up to suction), with the corresponding suction line 66 through other appropriate distribution windows 20, 44, 45 and 21.

Each group of displacers 7 of the same diameter equally spaced on the same diameter creates an independent flow between pairs of hydraulic lines 66 connected to one of the directional control valves 64 or 66. By setting, one or another combination of switching on the directional control valves 64 provides a different, stepwise varying value and direction of supply to hydraulic lines 10. For a given ratio of the areas of the displacers FI: F2: РЗ 1: 3: 9. including in different combinations the control valves 64 and folding or subtracting the initial flows in the hydraulic lines 66. x can receive thirteen stages of uniform supply to gidromagistrali 10 in each direction. This is illustrated by the table, which shows the working volumes (volumetric constants) of the pump sections, corresponding in the same way as the displacer areas 7 - qi: p2: pz 1: 3: 9. The direction of control of the directional control valve 64 in one direction or another is indicated or -, and its neutral position is O.

The total working volume of the adjustable part of the hydraulic pump is determined by the expression

q 2.1 P Smax -, -,, qi + q2 + q3

where q g: max

q2i qs: / qi:

qi qi / qi 1; q2 q2 / qi 3; q3 q3 / qi 9.

Then the stepwise regulated flow created by the hydraulic pump is determined by the expression

. Qi qsi n.

where n is the rotational speed of the shaft 24.

The proposed engine - a pumping unit in comparison with power units made on the basis of traditional engines with a crank kinematics and a crankshaft associated with a traditional pump, for example an axial piston, has undeniable advantages in that there is no energy transfer from the products to the power flow burn two liquid converting mechanisms to the liquid: a crank mechanism with a crankshaft in the engine and a non-inclined washer mechanism or an inclined () cylinder lock in the hydraulic pump. This reduces the dimensions, weight and material consumption of the power unit by 2–3 times, reduces losses in it due to the absence of intermediate transformations of movement from the pistons 4 of the engine to the displacers 7 of the hydraulic pump, and for the same reasons increases its durability, reliability, and efficiency.

Claims (11)

Formula 1, An engine-pumping unit comprising a housing with cylinders and pistons of an internal combustion engine arranged in a circle with uniform angular pitch parallel to the central axis, blocks of pump cylinders with hydraulic pump displacers disposed therein and directly connected to the engine pistons and forming pump chambers connected to the hydraulic power line via a switchgear, a piston synchronization mechanism made in the form of a swash plate, kinematically with connected with the piston rods of the engine and a non-power shaft, housed in a housing along a central axis on the bearing assemblies, as well as a gas distribution mechanism with intake and exhaust systems, a starting device, fuel-supplying equipment and auxiliary devices equipped with a drive from a non-power shaft, with no h But also with the fact that, in order to reduce axial dimensions, it is equipped with switching hydraulic plates located in the base of the housing, pump cylinder blocks and engine cylinders are connected to the hydraulic plates Among themselves, the engine cylinders are equipped with a common annular head and form combustion chambers oriented in one direction with it, the number of cylinders is chosen odd, at least three, in the annular head (fuel supply equipment is installed, the dispenser is made in the form of a rotating spool mounted on a non-powered shaft, and counter surfaces on switching hydraulic plates with distribution windows communicated with pump chambers and power hydraulic lines. 2. Pop assembly, 1, characterized in that the gas distribution mechanism is made in the form of valves placed in a common annular head. 3. The unit according to claim 1, with the exception of the fact that the exhaust system of the gas distribution mechanism is made of spool, and inlet valve. 4. Unit pop. 1, on the basis of the fact that the inlet system of the gas distribution mechanism is made of spool, and the exhaust - valve 5. The unit according to claims 2-4, characterized in that. that the valve timing mechanism is in the form of a cam. 6. The assembly according to claim 5, characterized in that the cam is face-mounted. 7. The unit according to p. 5, with the exception of the fact that the cam is made radial. 8. Unit pop. 1, characterized in that the rotating spool of the switchgear is cylindrical. 9. The unit according to paragraphs. 1, characterized in that the rotating spool of the switchgear is face-wise. 10. The unit according to paragraphs. 1, on the basis of the fact that the displacers of the hydraulic pump are located around the circumference around the rods pistons. 11. The unit according to paragraphs. 1, wherein the fuel supply device is equipped with a high pressure fuel pump with an annular body and radially arranged plungers, and the drive mechanism of the fuel pump plungers is made in the form of a radial cam mounted on a non-force shaft. 6 .622 ... 6f. (pus. 1 1775008 Aa S-ff Phi2. 2. BB az a.S e. 5 ... ... FIG. fO 3 g  .. / y 2