DE3331636A1 - AGGREGATE CONSISTS OF A PISTON PISTON AND A GEARBOX - Google Patents

Description

Patent attorneys Dipl ^ in-g. H: - \ ^ EiCKfciüiqrvDiPL.-PHYS. d _{r #} k. Fincke

Dipl.-Ing. EA. ¥ eickmann, Dipl.-Chem. B. Huber Dr.-Ing. H. Liska, Dipl.-Phys. Dr. J. Prechtel

^e 8000 MUNICH 86

POST BOX 860 820 λ λ «-ι λ λ λ

MDHLSTRASSE22 «** O IDOO

TELEPHONE (089) 98 03 52 TELEX 522621

Dr. med. Rabbe Nordström telegram godfather weickmannmonchen

Lohengrinstr. 8th
D-8022 Grünwald

transmission

The invention relates to a transmission, with a housing, a first gear part rotatably mounted in the housing, a second gear part mounted linearly displaceably in the housing Gear part and a cam gear, the cam track encloses the axis of rotation of the first gear part and its Cam follower is connected to the second gear part in such a way that the second gear part with constant Direction of rotation rotating first gear part executes a reciprocating displacement movement.

In known transmissions of this type is on the first, rotatably mounted in the housing gear part, for example one Shaft or the like, a cam attached, the peripheral surface of which forms the cam track. The curve follower is mounted so that it can be moved radially to the shaft. The known transmission thus requires a relatively large amount of space, in particular when both the outward movement and the forward movement of the cam follower are non-positively guided by the cam track shall be. In addition, the rotating cam generates unbalance vibrations.

It is the object of the invention to provide the cam mechanism explained at the beginning to be made smaller and essentially unbalance-free.

This object is achieved in that the second gear part coaxially to the first gear part rotatably mounted in the housing and non-rotatably but in the direction the axis of rotation is slidably coupled to the first transmission part so that the cam track is stationary on the housing is arranged and has increasing or decreasing thrust surfaces in the direction of the axis of rotation and that the Cam follower is rotatably connected to this with respect to the axis of rotation of the second transmission part.

In contrast to conventional cam drives, the cam follower moves while the cam track remains stationary. This avoids the imbalance of conventional cam gears. In addition, the moving masses are smaller than with comparable conventional cam gears. Since the Cam follower moved back and forth in the direction of the axis of rotation of the rotatable transmission part, are the dimensions of the Gearbox relatively small.

In a preferred embodiment, the first gear is involved as rotatable but axially fixed in the housing Gear formed. The second gear part comprises a rod elongated in the displacement direction with a polygonal cross-section, preferably triangular cross-section, which has an opening of the polygonal cross-section which is positively adapted Gear slidably interspersed. The rod can be mounted in a plain bearing of the gear in the opening of the gear, however, a linear roller bearing which guides the rod in a rotationally fixed but axially displaceable manner is arranged. The rolling elements are arranged eccentrically to the longitudinal plane of symmetry of the polygon surfaces in order to increase the torque to be able to transfer. The rolling elements can be axially free in cages, for example cages for endless rows of rolling elements, trade guided balls or cylinders;

the rolling elements can also be supported or guided on their own on axles of the rolling bearing.

The cam track expediently has at least one extending around the axis of rotation in the displacement direction rising thrust surface section and at least one extending around the axis of rotation, in the displacement direction sloping thrust surface section. The ascending and descending thrust surface sections are each provided in pairs and alternate in the circumferential direction away. The number of pairs of rising and falling thrust surface sections determines the number of lifting movements of the cam follower per revolution of the rotating gear part. Appropriately, at least two pairs are increasing and sloping thrust surface sections are provided. The ascending and descending thrust surface sections preferably point in opposite directions so that both the reciprocating motion of the curve follower is positively guided by the thrust surface sections.

The shape of the thrust surface sections can be conventional, in particular taking into account the acceleration ratios of the curve follower, for example in sinoid form, be chosen.

The transmission according to the invention is particularly suitable for the conversion of the rotary movement of a prime mover into the linear movement of the piston of a piston pump or else for converting the linear movement of the piston of a piston internal combustion engine into a rotating movement of a Output shaft. The piston of such a machine expediently runs in the direction of the axis of rotation rotatable transmission part, in particular coaxial with her.

Such piston pumps or piston internal combustion engines include inlet valves and outlet valves. The second gear part not only performs a shifting movement, but also rotates together with the first transmission part.

This rotary movement can be used to control rotary slide valves take advantage of their rotary slide coupled to the second transmission part in a rotationally fixed but axially displaceable manner are. For this purpose, the rotary slides are expediently arranged coaxially to the axis of rotation of the second gear part / for example on the end faces of the cylinders of the pump, which are also arranged coaxially with the second transmission part or internal combustion engine.

0 The piston pump or the piston internal combustion engine can at least comprise two separate piston-cylinder units / those in the direction of displacement of the second transmission part are arranged side by side. The piston-cylinder units can be on opposite sides of the Transmission be provided. In a preferred embodiment it is provided that the piston pump or the piston internal combustion engine has at least one cylinder / which is divided by the piston into two working spaces, the Rotary slide inlet valves and rotary slide outlet valves have rotary valve rotatably coupled to the second transmission part, such that both the inlet valves of the two Working spaces and the outlet valves of the two working spaces are alternately open or closed. These Embodiment is particularly advantageous for piston pumps / since here both the going and the going Piston stroke is used as a pump stroke. Such a piston pump has a high pumping capacity despite its small dimensions. In addition, the pulsations of the pumped fluid are low / if both working spaces are on the output side with one another are connected. The piston-cylinder arrangement explained above can be used in particular in four-stroke internal combustion engines insert. However, it can also be used as a two-stroke internal combustion engine.

Another two-stroke piston internal combustion engine , which can be used advantageously in connection with the transmission according to the invention, is known from DE-OS 30 29 287.

This internal combustion engine is designed as a two-stroke internal combustion engine and has three coaxially arranged one against the other sealed cylinder chambers, in each of which one of three over a piston rod in the direction of displacement firmly interconnected piston is slidably arranged. The middle cylinder chamber is through the middle one Piston divided into two spaces. The pistons each control valve slots of their cylinder chambers and, if necessary in connection with the piston rod, transfer channels between adjacent cylinder chambers. In this internal combustion engine the two outer cylinder chambers form the combustion chambers, while the middle cylinder chamber is divided into two supercharging chambers by the middle piston. These Arrangement leads to certain difficulties in the power take-off, since this is on the side of the "hot" combustion chambers he follows.

To avoid this disadvantage, it is preferably provided that the central piston, the central cylinder chamber in two Combustion chambers divided and at least one of the two combustion chambers common or several separate exhaust valve slots controls and that the two outer cylinder chambers provided with inlet valve slots supercharger chambers form that alternately feed the combustion chambers.

Such an internal combustion engine can also be used with another be operated as the aforementioned transmission. It can also be connected directly to the piston of a piston pump or other working machine, which can take advantage of the reciprocating movement of the three pistons, be directly coupled. The internal combustion engine is 0 here preferably firmly connected to the machine.

In the following, exemplary embodiments of the invention will be explained in more detail with reference to drawings. It shows

1 shows a schematic longitudinal section through a gear-5 piston pump unit;

FIG. 2 shows a cross section through the transmission piston pump unit of FIG. 1, seen along a line II-II; FIG.

3 shows a development of the inner jacket of a cylindrical housing part provided with a cam track the transmission piston pump unit of FIG. 1;

FIG. 4 shows a cross section through the transmission piston pump unit of FIG. 1, seen along a line IV-IV;

5 shows a longitudinal section through another embodiment a piston pump which can be used in the unit according to FIG. 1 and

6 shows a longitudinal section through a two-stroke internal combustion engine, in particular for use with a Transmission according to the transmission piston pump unit of FIG. 1.

The transmission piston pump unit shown schematically in FIG. 1 comprises a gear 1 and a piston pump 3 flanged to it. In a housing 5 of the gear 1 is rotatable an input shaft 7 is mounted on which a pinion 9 is seated in a rotationally fixed manner. The pinion 9 meshes with a gear 11, which is mounted axially on both sides on ball bearings 13 rotatably about an axis of rotation 15 in the housing 5.

.An elongated rod 17 interspersed with a triangular cross-section and flat polygonal surfaces 19, as best shown in FIG central opening 21 of the gear 11 • Linear rolling bearings guide the rod 17 in a rotationally fixed, but axially displaceable manner in the gear 11. The rolling elements 23 are for this purpose arranged eccentrically to the longitudinal plane of symmetry of each polygonal surface 19 in order to ensure the transmission of torque. The linear roller bearing can be a roller bearing in the manner of a spherical bushing with endless rows of rolling elements Act. The rolling elements 23 can, however, also be designed as axially mounted rollers or the like.

The rod 17 is connected in a rotationally fixed manner to a cam follower 25 of a cam gear 27. The curve follower 25 follows non-positively a cam path 31 provided as a groove on the inner casing of a hollow cylindrical housing part 29 Cam track 31 coaxially encloses the axis of rotation 15 of the gear 11 and thus the rod 17 and the cam follower 25. As best shown by the development of the inner jacket of the housing part 29 in FIG. 3, there is a curved path 31 off in the circumferential direction alternately in pairs

1Ό successive, rising thrust surface sections 33 and sloping thrust surface sections 35. The number of thrust surface section pairs determines the number of backward and backward movements of the cam follower 25 and thus the rod 17 per revolution of the gear 11. The increasing thrust

.15 surface sections 33 and the sloping thrust surface sections 35 point towards each other in the direction of the axis of rotation 15, so that both the forward movement and the backward movement of the cam follower 25 take place in a non-positive manner. the Curved path 31 can, for example, have a sinoid shape. In the illustrated embodiment, there are two pairs of thrust surface sections intended. Other pair numbers are possible. Likewise, the curve follower 25, as shown in FIG. 1, two diametrically opposite follower arms 37 which are rotatable at their radially outer ends about radial axes of rotation, in the cam 31 engaging rollers 39 carry. Even though a single one of these follower arms 37 is sufficient, as many follower arms as there are pairs of thrust surface sections are provided for better power transmission are.

The piston pump 3 includes a cylinder 41, in which a Piston 43 coaxial to the axis of rotation 15 is arranged displaceably in the direction of the axis of rotation 15. One rotatable The piston rod 45 of the piston 43, which is mounted on the cylinder 41, is firmly connected to the rod 17. The piston rod 45 carries sliding wedges 47, which are guided axially displaceably in axial grooves 49 of a rotary valve 51, and the pistons

Couple the rod 45 to the rotary slide valve 51 in a rotationally fixed but axially displaceable manner. The rotary valve 51 is rotatable, but axially fixed in front of an end face on the gate drive side of the cylinder 41 and has inlet slots 53 and outlet slots corresponding to the number of pairs of thrust surface sections 55, as can best be seen from FIG. 4, on. The inlet slots 53 control the connection an inlet port 57 of the cylinder 41 with an inlet channel 59. The outlet slots 55 control the connection an outlet port 61 and an outlet channel 63. The inlet slots 53 and outlet slots 55 are both shown in FIG Circumferentially and radially offset from one another in such a way that the inlet opening 57 and the outlet opening 61 are alternately open or closed.

The piston 43 can sit firmly on the piston rod 45, but it can also be rotatably mounted on the latter. At 65 In FIG. 1, a vent opening on the piston side of the cylinder 41 facing away from the rotary slide valve 51 is designated.

The gear-piston pump unit works as follows: When the input shaft 7 is rotated, the rod 17 Driven by the pinion 9 and the gear 11 with a constant direction of rotation about the axis of rotation 15. The one with the pole 15 axially fixed piston 43 performs, controlled by the cam gear 27, reciprocating stroke movements namely two complete stroke movements per revolution of the gear corresponding to the number of pairs of thrust surface sections

11. The rotary valve 45, which is non-rotatably coupled to the rod 17, opens at the beginning of the position shown in FIGS. 1 and 4 Suction phase the inlet port 57, while the outlet port 61 is closed. In the other reverse position of the cam gear 27, that is to say with two pairs of thrust surface sections after a quarter turn of the gear wheel 11, closes the rotary valve 51 the inlet port 57 and opens the outlet port 61.

• // 3-

Fig. 5 shows another embodiment of a piston pump 101, which can be driven via a gear 1 according to FIG. 1 instead of the piston pump 3. The piston pump 101 differs from the piston pump 3 of FIG. 1 essentially only in that its cylinder 103 by a Piston 105 is divided into two working spaces 107, 109, and the work rooms are controlled so that they alternate work in suction mode or alternately in pressure mode. One rotatable in the cylinder 103 and the piston 105 mounted piston rod 111 is in turn fixed to the Rod 17 of the transmission 1 connected. The working space 107 is controlled by a rotary valve 113 which is rotatable but axially fixed in front of the end wall of the cylinder 103 delimiting the working space 107, coaxially with the piston rod 111 is arranged. The piston rod 111 carries stationary sliding wedges 115 which are in axial grooves 117 of the rotary valve sit displaceably and couple the piston rod 111 in a rotationally fixed but axially displaceable manner with the rotary slide valve 113. The rotary valve 117 in turn has inlet slots 119 which connect an inlet opening 121 of the working space 107 to an inlet port 123 steer. Radially and angularly offset to the inlet slots 119 has the Rotary valve 113 outlet slots 125 which have an outlet opening 127 of the working space 107 with an outlet channel associate.

The piston rod 111 passes through the piston 105 and protrudes through the other working chamber 109 to the remote from the transmission Side of the cylinder 103. On this side, a mirror image of a further rotary valve 131 sits, which over Slide wedges 133 which are fixed to the piston rod and which are guided in axial grooves 135 of the rotary slide 131, but non-rotatably is coupled to the rotary valve 131 so as to be axially displaceable. The rotary valve 131 includes outlet slots 137 for control the connection of an outlet opening 139 of the working space 109 with an outlet channel 141 and inlet slots to control the connection of an inlet port 145 with

an inlet channel 147. The slots of the rotary valve 113 and 131 are arranged relative to one another in such a way that the pressure phases and suction phases alternate in each of the two working spaces 107, 109 in such a way that there is always only one of the two working spaces is operated in its suction phase and the other in its pressure phase.

The piston pump explained above differs from the piston pump of FIGS. 1 to 4 essentially only by the double use of its cylinder 103 by a piston 105 which phase shifted the cylinder 103 in two effective workspaces divided. For a further explanation, therefore, reference is made to the description of FIG. 1 referenced to 4. In detail, the cylinders 41 and 103 correspond, the pistons 43 and 105, the piston rods 45 and 111, the sliding wedges 47 and 115, 133, the guide grooves 49 and 117, 131, the rotary valves 51 and 113, 131, the inlet slots 53 and 119, 143, the outlet slots 55 and 125, 137, the Inlet ports 57 and 121, 145, the inlet channels 5 9 and 0 123, 147, the outlet ports 61 and 127, 139, and the Outlet channels 63 and 129, 141.

The basic construction of the piston pump shown in FIG. 5 can be used for an internal combustion engine, in particular a four-stroke internal combustion engine can be used. For a gasoline engine are indicated at 151 and 153 spark plugs, which do this via inlet ducts 123 and 141, e.g. from carburetors supplied air-fuel mixture, ignite alternately. 5 shows the combustion chamber 107 in the intake phase when it is open Inlet port 121. Inlet slots 119 and Outlet slots 125 of rotary valve 113 are arranged so that the combustion chamber is closed during the subsequent compression phase and the subsequent work phase is. The working phase is followed by the exhaust phase in which the outlet port 127 is open. The phases of the work space 109 running in the same order are opposite the phases of the work space 107 out of phase. In

the position according to Fig. 5, the working space is in the exhaust phase! in which the outlet port 139 is opened is. This phase is followed by the suction phase, the compression phase and finally the work phase. Instead of the exhaust phase of the working space shown in FIG. 5 109, through a suitable arrangement of the rotary slide valve 131, can also initiate the intake phase of the working chamber 107 the compression phase of the work space 109 can be assigned.

Fig. 6 shows a longitudinal section through a two-stroke internal combustion engine 201, the piston stroke movement of which is preferably converted into the Rotary movement of an output shaft is implemented. The piston stroke movement the internal combustion engine 201 can, however, also rotate through other gear constructions be implemented, or used directly to drive a work machine, in particular a piston pump.

The internal combustion engine 201 has three cylinder chambers 203, 205 and 207 arranged on the same axis next to one another on, in each of which a piston 209, 211 or 213 can be displaced in a sealed manner. The pistons 209, 211, 213 are axially fixed connected to a common piston rod 215. The middle one Piston 211 divides the middle cylinder chamber into two combustion chambers 217, 219 and controls one, if necessary a plurality of axially centrally arranged exhaust openings 221. The two outer cylinder chambers 203, 207 delimit on the one hand together with the pistons 209, 213 arranged therein and cylinder chamber partition walls 223 and 225, respectively, which are sealed off from the piston rod 215, and each of the supercharging chambers 227 and 229, respectively. The two outer pistons 209, 213 control inlet slots leading into the cylinder chambers 203, 207 231, 233. In the piston rod 215 are also between the central piston 211 and each of the two outer pistons 209 and 213 overflow channels 235 and 237 provided over the pre-compressed air or Pre-compressed mixture from the pre-compression rooms

or 229 can flow into the respective adjacent combustion chambers 217 and 219, respectively. For igniting the air-fuel mixture Spark plugs 239, 241 are provided in the combustion chambers 217, 219.

The combustion chambers 217, 219 are alternately loaded and flushed and alternately ignited. 6 shows the combustion chamber 217 at the moment of ignition. The inlet slot 231 is open so that the pre-compression chamber 227 is charged with fresh mixture. The work cycle drives the pistons in 6 to the right, the inlet slot 231 being closed and the fresh charge being compressed. The pre-compression pressure increases until the overflow channel 235 has migrated under the cylinder chamber partition 223 and the supercharging chamber 227 opens to the combustion chamber 217. This state is in FIG. 6 for the overflow channel 237 shown. The pre-compressed fresh mixture flows out of the pre-compression chamber 229 via the overflow channel 237 into the combustion chamber 219, while the exhaust gases flow out via the exhaust port 221. The rinsing process continues until the Reversing movement of the middle piston 211 closes the exhaust port 221 closes and the fresh charge is compressed again in the combustion chamber. The combustion chambers 217, 219 are ignited alternately. Furthermore, during the compression of the fresh charge in one of the combustion chambers, the fresh charge of the 'in each case other combustion chamber in the associated supercharger chamber. The pre-compression rooms are on the outside the combustion chambers arranged. This means that the combustion chambers can have relatively cool fresh charges despite the pre-compression be supplied even if the working temperatures of the Combustion chambers for the combustion of difficult to ignite fuels can be chosen higher. The power take-off elements, here the Piston rods 215 are led out of the housing of the internal combustion engine 201 on the “cooler” outside. the Internal combustion engine can work according to the Otto principle or the diesel principle. Die-pre-compression pressures and compression pressures can through suitable diameter ratios

of the middle piston 211 to the outer piston 209, to get voted. The pre-compression can be limited to the fresh air alone, while the fuel is injected directly into the combustion chambers 217, 219; however, a mixture can also be pre-compressed.

Claims (12)

P atentan sayings Gear, with a housing (5), a first gear part (11) rotatably mounted in the housing (5), a linearly displaceable in the housing (5) mounted second gear part (17) and a cam gear (27), whose cam track (31) encloses the axis of rotation (15) of the first gear part (11) and its cam follower (25) is connected to the second gear part (17) in such a way that the second gear part (17) with constant Direction of rotation rotating first gear part (11) performs a reciprocating displacement movement, characterized in that the second gear part (17) coaxially to the first gear part (11) rotatably mounted in the housing (5) and rotatably but in the direction of the axis of rotation (15) is coupled to the first gear part (11) that the cam track (31) is fixed on the housing (5) and rising in the direction of the axis of rotation (15) or sloping thrust surfaces (33, 35) and that the cam follower (25) with respect to the axis of rotation (15) of the second Gear part (17) is rotatably connected to this. 2. Transmission according to claim 1, characterized / that the first gear part is designed as a gear (11) rotatably but axially fixed in the housing is / that the second gear part is a rod (17) elongated in the sliding direction with a polygonal cross-section comprises, which is displaceable an opening of the gearwheel (11) which is positively adapted to the polygonal cross-section interspersed. 3. Transmission according to claim 2, characterized eichn e t that in the opening of the gear wheel (11) a the Rod (17) rotatably but axially displaceable leading linear roller bearing (23) is arranged. 4. Transmission according to one of claims 1 to 3, characterized / that the cam track (31) at least a thrust surface section that extends around the axis of rotation and increases in the direction of displacement (33) and at least one around the axis of rotation (15) extending and sloping in the direction of displacement Has thrust surface section (35), and that the rising and falling thrust surface sections (33, 35) are provided in pairs and extend in the circumferential direction alternate. 5. Transmission according to claim 4, characterized in that it is marked e t that the rising and the falling thrust surface sections (33, 35) point in opposite directions. 6. Transmission according to claim 4 or 5, characterized in that at least two pairs of increasing and sloping thrust surface sections (33, 35) are provided. 7. Transmission according to one of the preceding claims, characterized in that the second transmission part (17) is connected to a piston (43; 105; 209, 211, 213) of a piston pump (3; 101) or a piston internal combustion engine (101, 151, 153; 201) which can be displaced in the direction of the axis of rotation.
05 8. Transmission according to claim 7, characterized in that that the piston pump (3; 101) or the piston internal combustion engine (101, 151, 153) is a rotary slide inlet valve (53, 57; 119, 121, 143, 145) and a rotary slide outlet valve (55, 61; 125, 127, 137, 139), their rotary slide valves, which are preferably connected to one another (51; 113, 131) are rotatably arranged coaxially to the axis of rotation (15) of the second gear part (17) and that the second gear part (17) rotatably but axially movable with the rotary valve (s) (51; 113, 131) is coupled. 9. Transmission according to claim 7 or 8, characterized in that g e k e η η ze i chnet that the piston pump (101) or the piston internal combustion engine (101, 151, 153) has a cylinder (103) which through the piston (105) into two working spaces (107, 109) is divided, their rotary slide inlet valves (119, 121 or 143, 145) and rotary slide outlet valves (125, 127 or 137, 139) to the second gear part (17) coupled rotary valve (113 or 131), such that both the inlet valves (119, 121 or 143, 145) of the two working spaces (107, 109) as well as the outlet valves (125, 127 or 137, 139) of the two work spaces (107, 109) alternately are open or closed. 10. Transmission according to one of claims 8 or 9, characterized characterized in that the rotary slides (51; 113, 131) are arranged on cylinder end faces. 11. Transmission, in particular according to claim 7, wherein the piston internal combustion engine as a two-stroke internal combustion engine machine (201) is formed and three coaxially arranged / has mutually sealed cylinder chambers (203, 205, 207), in each of which one of three Pistons (209, 211, 213) which are fixedly connected to one another in the direction of displacement can be displaced via a piston rod (215) are arranged, the middle cylinder chamber (205) through the middle piston (211) in two Spaces (217, 219) is divided, and the pistons (209, 211, 213) valve slots (221, 231, 233) of their cylinder chambers (203, 205, 207) and, if necessary, in Connection to the piston rod (215) via flow channels (235, 237) between adjacent cylinder chambers (203, 205 or 205, 207), characterized in that the central piston (211) the middle cylinder chamber (205) divided into two combustion chambers (217, 219) and at least one two combustion chambers common or several separate outlet valve slots (221) controls and that the two outer Cylinder chambers (203, 207) with inlet valve slots (231, 233) form supercharging chambers (227, 229), which feed the combustion chambers (217, 219) alternately. 12. Transmission according to claim 11, characterized marked eichn e t that the maximum volume of the supercharger rooms (227, 229) is greater than the maximum volume of the axially adjacent combustion chamber (217, 219).