EP0097619A2 - Machine à pistons avec au moins deux pistons - Google Patents

Machine à pistons avec au moins deux pistons Download PDF

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Publication number
EP0097619A2
EP0097619A2 EP83810262A EP83810262A EP0097619A2 EP 0097619 A2 EP0097619 A2 EP 0097619A2 EP 83810262 A EP83810262 A EP 83810262A EP 83810262 A EP83810262 A EP 83810262A EP 0097619 A2 EP0097619 A2 EP 0097619A2
Authority
EP
European Patent Office
Prior art keywords
piston
yoke
machine according
eccentric
piston machine
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP83810262A
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German (de)
English (en)
Other versions
EP0097619A3 (en
EP0097619B1 (fr
Inventor
Guido Oberdorfer
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Individual
Original Assignee
Individual
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Individual filed Critical Individual
Priority to AT83810262T priority Critical patent/ATE30063T1/de
Publication of EP0097619A2 publication Critical patent/EP0097619A2/fr
Publication of EP0097619A3 publication Critical patent/EP0097619A3/de
Application granted granted Critical
Publication of EP0097619B1 publication Critical patent/EP0097619B1/fr
Expired legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/04—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
    • F04B1/0404—Details or component parts
    • F04B1/0426—Arrangements for pressing the pistons against the actuated cam; Arrangements for connecting the pistons to the actuated cam
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01B—MACHINES OR ENGINES, IN GENERAL OR OF POSITIVE-DISPLACEMENT TYPE, e.g. STEAM ENGINES
    • F01B1/00—Reciprocating-piston machines or engines characterised by number or relative disposition of cylinders or by being built-up from separate cylinder-crankcase elements
    • F01B1/06—Reciprocating-piston machines or engines characterised by number or relative disposition of cylinders or by being built-up from separate cylinder-crankcase elements with cylinders in star or fan arrangement
    • F01B1/062—Reciprocating-piston machines or engines characterised by number or relative disposition of cylinders or by being built-up from separate cylinder-crankcase elements with cylinders in star or fan arrangement the connection of the pistons with an actuating or actuated element being at the inner ends of the cylinders

Definitions

  • the present invention relates to a piston machine, with at least two pistons, and with an eccentric, which is mounted on the machine shaft and which can act on the base of the piston.
  • pumps with star-shaped pistons and cylinders use a less expensive solution.
  • There is an eccentric on the shaft which causes the pistons to move forward.
  • the pistons are then retrieved with the aid of compression springs which are arranged in the delivery chamber of the respective cylinder.
  • This solution has a number of disadvantages.
  • the pressure of the return springs must be overcome with each stroke, which results in energy losses.
  • Another disadvantage is that there is a fixed relationship between the speed of the pump and the magnitude of the pressure exerted by the springs. The faster the pump is to run, the greater the pressure that the springs must generate. For a certain type of spring there is therefore an upper speed at which the pump can still work.
  • the energy losses already mentioned are greater the faster the pump is to run.
  • the springs may not be able to return the piston.
  • the springs in the delivery chamber must be rustproof and resistant to chemicals. The feathers also interfere still the flow in the delivery chamber, cause large dimensions of the cylinder head, etc.
  • Machines of the type mentioned at the outset are also known, in which there is a bearing block on the eccentric in which at least one T-shaped groove is made. A plate is mounted in this groove, which is connected to the base of the piston.
  • the object of the present invention is to provide a piston machine in which the disadvantages mentioned do not occur.
  • a piston engine designed in this way can have three or more pistons arranged in a star shape, both of which Assembly of such a machine and its maintenance can be carried out very easily.
  • the machine shown in the drawings is a pump which is attached to an electric motor and which is driven by this electric motor.
  • the piston machine has a housing 2 which is fastened to the housing of the electric motor 1 by means of screws 3.
  • the machine housing 2 has a cavity 4 in which the drive elements for the pistons 5 of the machine are accommodated.
  • the pistons 5 accommodated in cylinders 6 are arranged in a star shape along the circumferential part of the cavity 4 in the machine housing 2.
  • the aforementioned cavity is closed at the front with the aid of a cover 7, which is fastened to the housing 2 with screws 8 so that it can be removed.
  • the end 9 of the shaft of the electric motor 1 which drives the pump is mounted in a bearing 10 which also serves as the bearing for the pump.
  • An eccentric 11 is plugged onto the machine shaft 9 and coupled to the shaft 9 by means of a wedge 12 (FIG. 3). If you want to change the stroke of the piston 5 and thus also the flow rate of the pump, you can replace the eccentric 11 with a differently shaped eccentric.
  • the piston engine is provided with a return device 14 which engages the foot part 15 of the piston 5.
  • This return device 15 has a base body 16 which is mounted on the eccentric 11. Furthermore, the return device 15 has claws 17 on the foot par tie 15 the piston 5 attack.
  • the base body 16 is ring-shaped.
  • the return claws are designed as extensions of the base body 16, which are distributed on the peripheral part of the ring 16 and which run away from the latter in the radial direction. The ends of these extensions are bent to one side, and this gives the claws 17 their shape.
  • These bent portions 18 of the extensions engage the foot portion 15 of the piston 5.
  • the foot part 15 of the piston 5 can be provided with a corresponding recess (not shown).
  • the foot part 15 of the piston 5 is provided with a shoe 19.
  • This shoe 19 has a plate 20 which rests on the sleeve 13.
  • the piston shoe 19 also has a clamp 21 (see e.g. Fig. 2) which is integral with the foot plate 20 and in which the end part of the piston 5 is clamped.
  • the piston 5 can be made of metal or a ceramic material.
  • the base plate 20 rests with its underside on the sleeve 13.
  • the return claw 17 engages on the upper side of the foot plate 20.
  • the forward movement of the piston 5 is thus caused by the sleeve 13 seated on the eccentric 11, on which the foot plate 20, however, only rests.
  • the backward movement of the piston 5, however, is caused by the claw 17 of the return device 14. Because the base body 16 of the return device 14 is mounted on the eccentric 11, so that this device carries out the same movement as the sleeve 5 driving the piston 13. Since the bent part 18 of the claw 17 engages on the upper side of the foot plate 20, it remains Foot plate 20, even if it performs the backward movement, in contact with the sleeve 13.
  • the base plate 20 has a section 26 which is extended towards the return device 14 and on which the return claw 17 engages.
  • 6 shows a particularly advantageous embodiment of the sleeve 13.
  • the outside of the sleeve 13 is provided with projections 27, in the apex region of which there is a sliding surface 28.
  • This sliding surface 28 acts on the underside of the foot section 15 of the pistons 5.
  • the sliding surface 28 acts on the underside of the footplate 20.
  • the dimension of the respective sliding surface 28 in the circumferential direction of the sleeve 13 is advantageously smaller than the corresponding dimension of the underside of the footplate 20.
  • the sliding surface 28 and the underside of the footplate 20 form one Bearings.
  • the sleeve 13, which has the mentioned sliding surfaces 28, and the eccentric 11 together form a sliding bearing.
  • the interior 4 in the housing 2 is normally filled up to about half with oil.
  • the sliding surfaces mentioned have a very advantageous effect in such circumstances because, thanks to their size and the oil film between them, they absorb such a load relatively softly and therefore have a dampening effect. This also creates better conditions in the event of an emergency run.
  • the clamp 21 in the region of the bent part 18 of the claw 17 can be provided with a cutout 29 (FIGS. 1 and 2) into which the bent part 18 of the return claw 17 engages .
  • the return device which is designed as a yoke that connects the two pistons to one another, bridges the eccentric 11.
  • One end of the respective piston is mounted in the ends of this yoke.
  • the end of the respective piston is with a guide metal plate.
  • the yoke is also U-shaped, parts of the bottom of the yoke, which is U-shaped in cross section, being removed in the end parts of the yoke.
  • the free-standing side walls of the yoke are each provided with a slot in which the guide plate of the respective piston is mounted.
  • connection between the guide plate and the piston is achieved in this known machine in that a blind hole with a thread is made in the piston end.
  • the guide plate is provided with a threaded bolt that is screwed into the blind hole of the piston.
  • connection point of the ceramic piston with the metal pin is subjected to great forces during operation of the pump, the direction of which also changes rapidly. This can destroy this connection point and thus lead to a premature failure of the pump.
  • the yoke is actually only loosely seated on the guide plates of the pistons, so that the slots between the guide plates and the slots in the yoke can increase considerably over time. This can destroy the yoke and thus also lead to the failure of the pump.
  • the Ge consists of the yoke and the two pistons add only a little stiffness so that vibrations can occur in the pump.
  • the piston machine shown in FIG. 7 is designed as a piston pump.
  • a drive shaft 102 is rotatably mounted in a housing 101.
  • This shaft 102 is provided with an eccentric disk 103 on which an intermediate piece 104 is mounted.
  • This intermediate piece is designed as a slide ring.
  • the pump has two horizontally arranged and diametrically opposite pistons 105, which are made of a ceramic material. These pistons 105 have the shape of a cylindrical rod and are each mounted in a cylinder 106 so as to be longitudinally displaceable.
  • a cylinder head 107 is connected to the respective cylinder 106, in which valves (not shown) are accommodated.
  • the respective cylinder head 107 is also provided with connections (not shown) for a suction line and for a pressure line (not shown).
  • a yoke 110 which is U -shaped and serves as the return device.
  • the cross section of the yoke 110 is also U -shaped, so that parts of the slide ring 104 can be located in the yoke.
  • the end parts of the legs 111 of the U-shaped yoke 110 are provided with clamping devices 112, in which the pistons 105 are fastened at one end. Rigid holding of the pistons 105 in the respective clamping device 112 is achieved with the aid of screws 113.
  • the end of the respective piston 105 facing the eccentric 103 is provided with a blind hole 114.
  • this blind hole 114 there is a bolt 115 which is fastened to a plate 116 made of metal. With one of its sides, this plate 116 rests on the end face of the piston end. The other side of the plate 116 can come into contact with the slide ring 104, which is located on the eccentric 103, during operation of the pump.
  • the plate 116 can represent the bottom of a sleeve. This cap-shaped structure is placed on the end of the piston 105 facing the eccentric 103.
  • the piston 105 can also be designed as a sleeve.
  • the mouth of such a sleeve is covered by the plate 116, the pin 115 being located inside the sleeve-shaped piston for the purpose of guiding the plate.
  • the slide ring 104 on the eccentric disk 103 first pushes the right piston 105 to the right by exerting pressure on the plate 116. Since the yoke 110 is fastened to the right piston 105 with the aid of the right clamping device 112, the yoke 110 also moves to the right. At the other end of the yoke 110, the left piston 105 is fastened with the aid of the left clamping device 112. As a result, the left piston 105 now also moves to the right. After the eccentric 103 has reached its extreme right position, he begins to apply pressure to the plate 116 of the left piston 105.
  • the yoke 110 shown in FIG. 8 corresponds to the yoke shown in FIG. 7, further details of this yoke being apparent from FIGS. 9 to 11.
  • this yoke 110 is U-shaped, and its legs 111 are each provided with a clamping device 112 for the pistons 105.
  • the cross section of the yoke is also essentially U-shaped, as can be seen from FIGS. 9 to 11.
  • the clamping device 112 has an essentially annular portion 120, one end of the respective piston 105 being located in the opening 121 of this annular portion 120.
  • This annular portion 120 is interrupted by a slot 122.
  • the ring 120 thus interrupted can thus spring.
  • the yoke shown in the drawings is designed as a casting, although it also e.g. can be made of sheet metal.
  • the ends of the annular portion 120 have material piles 123, these material piles 123 being provided with bores 124 and 125.
  • the lower bore 125 is provided with a thread 126 with which the thread of the screw 113 (FIG. 7) is engaged.
  • the U-shaped yoke of the type described would nevertheless have a certain flexibility, so that the structure consisting of the yoke and the pistons would not be as rigid as the vibration-free operation of the machine requires.
  • the yoke or the connecting piece can be designed as shown in FIG. 12.
  • the yoke 130 according to FIG. 12 has two end walls 131 lying parallel to one another, of which only the front end wall can be seen in FIG. 12.
  • the end walls 131 are connected to one another by means of side walls 132, which are shorter than the end walls 131.
  • the end walls 131 each have an opening 133 through which the shaft 102 carrying the eccentric 103 can pass.
  • the side walls 132 of this yoke are provided with the already mentioned clamping devices 112 for the pistons 105.
  • the opening 121 in the annular portion 120 of the clamping device 112 continues in the side wall 132 of the yoke 130. In this case too, the annular portion 120 has the slot 122 through which the screw mentioned (not shown here) passes.
  • the respective piston is thus fastened in this yoke 130 in the manner already described.
  • this yoke Since the pistons 105 are connected to one another with the aid of an upper part 134 and a lower part 135 of the yoke 130, this yoke has an extraordinarily high rigidity, and the structure consisting of the pistons and this yoke is very rigid.
  • the yoke 130 can also be designed such that the upper part 134 and the lower part 135 form two parts which, in order to be able to form the yoke, are screwed together by means of four screws 113.
  • Each of the yoke halves. 134, 135 then only has a section of the annular part of the clamping device 112, but at the two ends of the respective section of the annular part there is a material accumulation (not shown) through which the screws 113 pass, or in which these Screws are screwed in.
  • the pistons can also be arranged side by side in rows. Adjacent piston may be driven by a plurality on a common K originally belwelle 102 seated eccentric.
  • the yoke 130 shown in FIG. 12 also offers the possibility of providing its side walls 132 with a plurality of clamping devices 112, so that the pistons are then one above the other, for example. In such a case, only a single eccentric and a single yoke is sufficient to drive several pistons.
  • FIG. 13 shows a further development of the machine according to FIG. 7.
  • This machine in turn has a U-shaped yoke 110, but the part 137 of the leg 136 connecting this yoke is provided with reinforcing ribs 138.
  • These ribs 138 increase the rigidity of the yoke 110.
  • the design and the arrangement of the reinforcing ribs 138 can be seen clearly from FIG. 14.
  • the reinforcing ribs 138 are located on the outside of the connecting part 137. If necessary, such ribs can also be located on the inside of the connecting part 137.
  • One of the consequences of using such ribs is that the bending stress on the pistons 105 in the region of the clamping device 112 is reduced. In addition, this measure contributes to the machine runs more smoothly, especially when the machine is running at high speed.
  • the intermediate piece which is located between the eccentric 103 and the piston 105, is designed as a sliding block 140 in this embodiment of the machine.
  • the respective flat surface 141 of the sliding block 140 faces the eccentric end of the piston 105.
  • the use of the sliding block 140 has the advantage that the contact area between the sliding block 140 and the piston 105, or the plate 116 upstream of the piston 105, is large, a lubricating film being able to form between them. As a result, the moment transmitted from the eccentric to the piston can be greater without overstressing the material of these components.
  • the plate 116 is also designed differently.
  • This plate 116 has extensions 142 which rest in grooves 143. These grooves 143 are made in the inside of the legs 136 of the yoke 110.
  • the plate 116 is flat on both sides and is held in place by means of its runners 142.
  • One flat surface of this plate 116 lies on the piston 105, while the other flat surface is under the action of the sliding block 140.
  • the plate l16 has a square plan.
  • FIG. 15 shows a further possibility of how the piston 105 can be fastened in the yoke.
  • the inner wall of the annular portion 120 is provided with a conical thread into which a collet nut 144 is screwed.
  • the collet nut 144 is shown separately in FIG. 16. It has a flat section 145, the circumference of which is hexagonal. This part can be attacked with a key and thereby the mother 144 into the Screw in the yoke.
  • This flat part 145 is followed by tongues 146, the outside of which is provided with a corresponding thread.
  • the inside of the annular portion 120 may be provided with a support surface 147.
  • This further embodiment of the clamping device has a pressure element 148 which contains a tubular section 149.
  • the flange 150 of this element is provided with openings through which screws 151 pass, which are screwed into the yoke 110.
  • An annular clamping element 152 is located between the end face of the tubular part 149 and the bearing surface 147. By tightening the screws 151, the clamping element is compressed, so that the diameter of the opening in the clamping element 152 is reduced and the piston is thereby held in the clamping device.
  • the annular portion 120 of the yoke 110 is designed as a piece of pipe, the wall of the piece of pipe being provided with an opening 154 having a thread.
  • a clamping screw 155 is screwed whose tip penetrates into the material of the piston 105th
  • the forces returning the piston 105 act on the surface of the piston.
  • the area on which the above-mentioned forces now act is larger than the area that was previously available in the area of the screw connection between the threaded bolt and the piston.
  • the piston 105 is now held in a clamp 112, whereas previously only used a screw connection between the piston and the pin.
  • the structure consisting of the yoke 110 and at least one piston 105 has a much greater rigidity, so that vibrations can hardly occur.
  • the bolt 115 which forms a whole with the plate 116 can also be screwed into the piston 105, but this bolt 115 is advantageously only pushed into the piston 105. Because this connection point is only subjected to pressure because the piston 105 is returned with the aid of the yoke 110 acting on the piston body.
  • a so-called blind piston (not shown) can be fastened in the yoke instead of one of the pistons.
  • This blind piston can be designed as a short rod that is clamped in the other clamping device. The end of this rod facing the eccentric is provided with a plate which has already been described in connection with the machine according to FIG. 1.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Reciprocating Pumps (AREA)
  • Details Of Reciprocating Pumps (AREA)
EP83810262A 1982-06-18 1983-06-15 Machine à pistons avec au moins deux pistons Expired EP0097619B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT83810262T ATE30063T1 (de) 1982-06-18 1983-06-15 Kolbenmaschine mit wenigstens zwei kolben.

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
CH3756/82 1982-06-18
CH375682 1982-06-18
CH429482 1982-07-15
CH4294/82 1982-07-15

Publications (3)

Publication Number Publication Date
EP0097619A2 true EP0097619A2 (fr) 1984-01-04
EP0097619A3 EP0097619A3 (en) 1984-10-10
EP0097619B1 EP0097619B1 (fr) 1987-09-30

Family

ID=25693779

Family Applications (1)

Application Number Title Priority Date Filing Date
EP83810262A Expired EP0097619B1 (fr) 1982-06-18 1983-06-15 Machine à pistons avec au moins deux pistons

Country Status (4)

Country Link
US (1) US4589329A (fr)
EP (1) EP0097619B1 (fr)
DE (1) DE3373926D1 (fr)
SU (1) SU1570657A3 (fr)

Families Citing this family (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB9217208D0 (en) * 1992-08-13 1992-09-23 Weeja Compressors Limited Improvements in compressors
GB2272732B (en) * 1992-10-08 1997-02-05 Gordon William Walke High pressure water pump
DE4443868A1 (de) * 1994-12-09 1996-06-13 Teves Gmbh Alfred Radialkolbenmaschine
DE102005055057A1 (de) * 2005-11-18 2007-05-24 Robert Bosch Gmbh Mehrkolbenpumpe
EP2031247A1 (fr) * 2007-08-31 2009-03-04 Pfizer Inc. Pompe liquide
SE540991C2 (sv) * 2013-11-25 2019-02-19 Thordab Ab Pump/motor innefattande en växelfunktion
CN115298435A (zh) * 2019-12-05 2022-11-04 费罗尼变速箱有限责任公司 对流体施加压缩作用的泵和由对应推进流体驱动的马达

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB740784A (en) * 1953-08-17 1955-11-16 Lucas Industries Ltd Reciprocatory pumps
GB879285A (en) * 1958-06-22 1961-10-11 Andrew Fraser Improvements in and relating to radial-piston hydraulic pumps
CH360591A (fr) * 1959-04-16 1962-02-28 Norton Tool Company Limited Machine à piston
DE1528504A1 (de) * 1966-10-05 1970-07-02 Guido Oberdorfer Fa Einrichtung an Kolbenpumpenantrieben
DE2748620A1 (de) * 1977-10-29 1979-05-03 Oberdorfer Guido Kolbenpumpe

Family Cites Families (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3125034A (en) * 1964-03-17 Pump with radial cylinders
US1964245A (en) * 1931-09-22 1934-06-26 Hydraulic Press Mfg Co Constant delivery radial piston pump
US2324291A (en) * 1942-06-15 1943-07-13 Hydraulie Controls Inc Pump
US2679808A (en) * 1949-04-22 1954-06-01 Bernard M Thun Fluid pressure generator
US2801596A (en) * 1953-04-02 1957-08-06 Sewell Ronald Percival Multi-cylinder pump
FR1287601A (fr) * 1961-02-03 1962-03-16 Rech Etudes Prod Moteur hydraulique
US3413929A (en) * 1966-04-21 1968-12-03 Hypro Inc Radial piston pump
US3924968A (en) * 1972-07-27 1975-12-09 Gen Motors Corp Radial compressor with muffled gas chambers and short stable piston skirts and method of assembling same

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB740784A (en) * 1953-08-17 1955-11-16 Lucas Industries Ltd Reciprocatory pumps
GB879285A (en) * 1958-06-22 1961-10-11 Andrew Fraser Improvements in and relating to radial-piston hydraulic pumps
CH360591A (fr) * 1959-04-16 1962-02-28 Norton Tool Company Limited Machine à piston
DE1528504A1 (de) * 1966-10-05 1970-07-02 Guido Oberdorfer Fa Einrichtung an Kolbenpumpenantrieben
DE2748620A1 (de) * 1977-10-29 1979-05-03 Oberdorfer Guido Kolbenpumpe

Also Published As

Publication number Publication date
EP0097619A3 (en) 1984-10-10
SU1570657A3 (ru) 1990-06-07
DE3373926D1 (en) 1987-11-05
EP0097619B1 (fr) 1987-09-30
US4589329A (en) 1986-05-20

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