EP1715183B1 - Pompe hydraulique à pistons axiaux - Google Patents

Pompe hydraulique à pistons axiaux Download PDF

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Publication number
EP1715183B1
EP1715183B1 EP06015437A EP06015437A EP1715183B1 EP 1715183 B1 EP1715183 B1 EP 1715183B1 EP 06015437 A EP06015437 A EP 06015437A EP 06015437 A EP06015437 A EP 06015437A EP 1715183 B1 EP1715183 B1 EP 1715183B1
Authority
EP
European Patent Office
Prior art keywords
cylinder block
cylinder
axial piston
piston pump
valve
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.)
Expired - Lifetime
Application number
EP06015437A
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German (de)
English (en)
Other versions
EP1715183A3 (fr
EP1715183A2 (fr
Inventor
Markus Berger
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.)
Bieri Hydraulik AG
Original Assignee
Bieri Hydraulik AG
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 Bieri Hydraulik AG filed Critical Bieri Hydraulik AG
Priority to AT06015437T priority Critical patent/ATE403804T1/de
Priority to EP06015437A priority patent/EP1715183B1/fr
Priority to DE50212619T priority patent/DE50212619D1/de
Publication of EP1715183A2 publication Critical patent/EP1715183A2/fr
Publication of EP1715183A3 publication Critical patent/EP1715183A3/fr
Application granted granted Critical
Publication of EP1715183B1 publication Critical patent/EP1715183B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime 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
    • F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F04B1/14—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis having stationary cylinders
    • F04B1/141—Details or component parts
    • F04B1/143—Cylinders
    • 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
    • F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F04B1/14—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis having stationary cylinders
    • F04B1/141—Details or component parts
    • F04B1/145—Housings
    • 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
    • F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F04B1/14—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis having stationary cylinders
    • F04B1/18—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis having stationary cylinders having self-acting distribution members, i.e. actuated by working fluid
    • F04B1/182—Check valves

Definitions

  • the invention relates to a hydraulic (ie suitable for conveying a liquid) axial piston pump, which is particularly suitable for use as a feed pump for a fuel oil burner.
  • a pump of the type mentioned is from the EP-A1-0 180 510 known.
  • the pump described in this document has a provided with a hollow cylinder cylinder block.
  • a arranged outside the cylinder block swash plate moves by means of a piston rod which passes through an open base of the hollow cylinder, a delivery piston in the hollow cylinder periodically back and forth.
  • the delivery piston By the movement of the delivery piston, the volume of a delivery chamber is changed periodically.
  • the delivery chamber is bounded by the other (also referred to as the front), substantially closed base surface of the hollow cylinder, which is facing this side facing the delivery piston and a part of the lateral surface of the hollow cylinder.
  • the delivery chamber is intended for receiving and further conveying the liquid to be conveyed or pumped, the periodic change of the delivery chamber volume causing the actual pumping process.
  • the piston movement in the sense of an enlargement of the delivery chamber volume is referred to as a suction stroke, while the piston movement in the sense of a reduction of the delivery chamber volume is referred to as a pressure stroke.
  • An inflow line for the liquid to be conveyed opens through the conveyor piston opposite the front base of the hollow cylinder through into the delivery chamber.
  • suction valve suction valve is arranged, which is pressed by means of a closing spring in its closed position.
  • the closing spring according to EP-A1-0 180 510 further coupled via a control linkage with the swash plate.
  • the liquid is conducted from the delivery chamber through an outflow line into a valve chamber formed in the cylinder block, in which a pressure valve designed as a check valve is arranged. From the valve chamber, the liquid flows past the pressure valve to an outlet opening on the outside of the cylinder block.
  • the object of the invention is to improve a generic axial piston pump such that it has a simple construction and a small space requirement.
  • an axial piston pump for conveying a liquid comprises a cylinder block which has at least one outer surface which, at least in one part, has the shape of a lateral surface of a cylinder.
  • a delivery piston is displaceably arranged such that between the walls of the hollow cylinder and an end face of the delivery piston, a delivery space for receiving the liquid to be delivered is enclosed.
  • the axial piston pump further comprises a discharge line leading away from the delivery chamber for the liquid to be conveyed, which is designed as a channel in the cylinder block and leads from the delivery chamber to the at least one cylindrical jacket-shaped part of the outer surface of the cylinder block.
  • the axial piston pump finally comprises a non-return valve serving as a pressure valve, the valve seat of which is arranged in a section of the channel of the discharge line which is directly adjacent to the cylindrical jacket-shaped part of the outer surface of the cylinder block.
  • a made of an elastic material ring or C-shaped, along a circumferential line of the cylinder jacket-shaped portion of the outer surface of the cylinder block extending closing spring element is arranged such that it acts as a closing spring for the pressure valve.
  • the outer surface of the cylinder block can in particular have the shape of a lateral surface of a straight circular cylinder.
  • the outer surface in this game but also have another suitable cylinder jacket shape, for example, the shell shape of an elliptical cylinder.
  • "along a circumferential line” means either along a circumferential line (or a circumferential line section) on the outer surface of the cylinder block or along a groove along a circumferential line (or a circumferential line portion) is formed in the outer surface of the cylinder block.
  • a ring-shaped or C-shaped elastic closing spring element allows easy manufacture and assembly of the closing spring of the pressure valve and thus a cost-effective and compact construction of the axial piston pump.
  • the pressure valve may either be formed as a valve seat itself adjacent to the outer surface of the cylinder block channel portion, or it may be a separate valve seat member inserted into this channel section.
  • the arrangement of the valve seat in the immediate vicinity of the outer surface of the cylinder block allows easier access to the valve seat, which is advantageous for the assembly and for any revisions of the pump.
  • the outflow line of only one side (namely, the outer surface of the cylinder block) is formed as a channel in the cylinder block, a simple production of the axial piston pump is made possible.
  • the channel may be punctured, in particular as a straight channel, e.g. be carried out by drilling or other suitable Abtragungsvon in the cylinder block.
  • the arrangement of the mouth of the discharge line in the delivery chamber (also referred to as outlet of the delivery chamber) in the immediate vicinity of the front base and thus the mouth of the inflow in the delivery chamber (also referred to as an inlet into the delivery chamber) for an extremely small dead volume.
  • a small dead volume allows the pump to be used for comparatively high suction heights, reduces the formation of air bubbles in the fluid delivered by the pump, and ensures efficient operation of the pump.
  • a suction valve is understood to be a valve which permits the liquid flow in the inflow line in the direction of the delivery chamber upstream of the delivery chamber, but in the opposite direction (ie away from the delivery chamber).
  • a pressure valve is understood to be a valve which permits the liquid flow in the outflow line in the direction away from the pumping chamber downstream of the pumping chamber, but in the opposite direction (ie towards the pumping chamber).
  • a channel which leads directly from the pumping chamber to the outer surface of the cylinder block, a channel is to be understood, which leads from the pumping chamber without passage through any other chambers or cavities through directly to the outer surface, in contrast, for example, to the in EP-A1-0 180 510 described discharge line, which leads from the delivery chamber initially in a valve chamber and only from this to the outside of the cylinder block.
  • the channel of the discharge line is even formed such that it leads on the shortest path from the hollow cylinder to the outer surface of the cylinder block. This creates a particularly small dead volume.
  • the channel leads to deviating paths from the shortest path, either straight or along curves, from the hollow cylinder to the outer surface of the cylinder block.
  • the delivery piston has a circumferential reduction in an axial region in the vicinity of its front side facing the front base surface of the hollow cylinder.
  • a reduction in size is understood that the circumference of the delivery piston in an axial region is smaller than the substantially corresponding to the hollow cylinder circumference in the vast remaining area of the delivery piston.
  • an annular channel also referred to as an annular channel
  • the circumferential reduction is arranged in an axial region of the delivery piston such that it is arranged at maximum compression (ie with minimal volume of the delivery chamber) at least partially above the mouth of the outflow channel in the lateral surface of the hollow cylinder.
  • the liquid can then flow from the delivery chamber through the annular channel directly through the outlet of the delivery chamber into the discharge channel.
  • the delivery piston in the hollow cylinder can be pushed all the way to the front during the pressure stroke, so that in the position with maximum compression, the end face of the delivery piston is arranged in the immediate vicinity of the front base of the hollow cylinder.
  • its front end side can be arranged partially or even completely in front of the mouth of the outflow line. It is ensured by the annular channel that the liquid can nevertheless still flow out of the delivery chamber through the outflow channel. Overall, the annular channel allows a further reduction of the dead volume.
  • the circumferential reduction may be formed in the foremost axial region of the delivery piston which adjoins the front end side of the delivery piston.
  • a check valve serving as a suction valve which has a shut-off body with a flat portion, arranged in the axial direction immediately before the hollow cylinder such that the flat portion forms a part of the boundary wall of the pumping chamber in the closed state of the suction valve.
  • the flat part of the shut-off is formed as an integral part of the delivery chamber boundary wall, there is a particularly small dead volume.
  • the directed to the delivery chamber side of the flat portion of the shut-off can in particular be designed and arranged such that it forms a part of the front base of the hollow cylinder in the closed state of the suction valve.
  • other suitable suction valves for the inventive axial piston pump can be used.
  • the cylinder block is arranged on a selectively replaceable type in a pump housing which at least partially surrounds it such that the outer surface of the cylinder block is enclosed by the pump housing in the region of the discharge line (ie in the region of the mouth of the discharge line in the outer surface) is.
  • the pressure valve may be arranged at least partially outside the cylinder block in the pump housing. It can e.g. the closing spring element of the pressure valve and / or a shut-off body of the pressure valve may be arranged in the pump housing outside the cylinder block.
  • pressure valve components are arranged, which are subject to a comparatively small wear during operation of the pump. This makes it possible to replace in the course of a revision of the pump, only the cylinder housing together with the parts arranged therein, which are subject to a relatively large wear, while the pump housing and the parts arranged therein can be used.
  • the entire cylinder block may be formed as a one-piece molding to allow a quick and easy replacement of the cylinder block.
  • it is made of a comparatively wear-resistant material in order to increase its service life.
  • the pump housing can be made of a less wear-resistant, but better machinable material, since it is subject to a much smaller wear than the mechanically highly stressed cylinder block.
  • the cylinder block is formed such that its outer surface at least in a portion which includes the mouth of the channel of the discharge line in the outer surface, the shape of a lateral surface of a right circular cylinder and in this circular cylindrical shell a parallel to the hollow cylinder axis cylinder block axis (namely, the cylinder axis of circular cylindrical lateral surface) defined.
  • the outer surface of the cylinder block can be made by turning on a machine tool.
  • Next can in the cylinder block for cylindrical shell surface parallel hollow cylinder can be easily produced by drilling.
  • the axial piston pump has two or more pressure valves, these may be designed and arranged such that the closing spring element acts as a common closing spring for these pressure valves.
  • the pressure valves may in particular be provided with valve seats, which are arranged substantially in the radial direction within a certain circumferential line of the cylinder jacket-shaped portion of the outer surface of the cylinder block, wherein this circumferential line is that which extends along the closing spring element.
  • the closing spring element is designed and arranged such that it simultaneously acts as a shut-off of the pressure valve or the pressure valves.
  • the construction of the axial piston pump can be further simplified.
  • the closing spring element is even designed and arranged so that it acts simultaneously as the sole closing spring and the only shut-off for the pressure valve or valves, the valve seats are arranged radially within him in the cylinder block.
  • a diffusion element also referred to as a mixing element which causes a reduction in the size of any gas bubbles present in the liquid can be arranged upstream in the inflow line immediately upstream of the suction valve.
  • the diffusion element ensures a mixing of the medium flowing through it. If gas bubbles are present in the liquid to be conveyed, the diffusion element ensures a mixing of these gas bubbles with the liquid and thus a reduction of the gas bubbles.
  • gas bubbles In particular, air bubbles can occur when the pressure in the inflow line is comparatively small, which is the case in particular for comparatively large suction heights (ie, large heights of the pump above the liquid level of the liquid to be suctioned by the axial flow pump through the inflow line). At suction heights of typically over three meters there is a risk that air will be released from the aspirated liquid and form bubbles in the liquid. Without a diffusion element, the bubbles can reach a size which necessitates venting of the delivery chamber, which leads to pump failure, since the delivery chamber must be vented against pressure via the suction valve.
  • the diffusion element may be a filter element made of a sintered material or a fine mesh screen.
  • Such diffusion elements are particularly simple and inexpensive. In principle, however, it is also possible to use other suitable diffusion elements which ensure effective reduction of any gas bubbles which may be present in the liquid.
  • Fig. 1 an axial piston pump is shown in a simplified cross-sectional partial view. It serves for a better understanding of the invention, as described below in connection with the FIGS. 2 and 3 is shown.
  • Axialkolbenpumpe shown serves for conveying fuel oil in a heating system for a building. It comprises a cylinder block 10 whose outer shape substantially corresponds to the shape of a straight circular cylinder and is formed by a circular cylindrical lateral surface and two circular base surfaces. By the circular cylindrical surface a cylinder block axis 12 is defined, namely the axis of the circular cylinder.
  • the cylinder block 10 is integrally formed and made of a comparatively wear-resistant steel. It is arranged in a cylinder block 10 completely comprehensive pump housing 14, 16, which is made of Antikorrodal, a material that is less resistant to wear than steel, but better machinable than steel.
  • the pump housing 14, 16 is composed of a first pump housing part 14 and a second pump housing part 16 optionally disassembled again.
  • the cylinder block 10 is selectively releasably attached to the first pump housing part 14 by means of a screw bolt 18 leading through a bore along the cylinder block axis 12 such that it can be dismantled and replaced by the pump housing 14, 16 as required after disassembly.
  • a screw bolt 18 leading through a bore along the cylinder block axis 12 such that it can be dismantled and replaced by the pump housing 14, 16 as required after disassembly.
  • Next are in the circular cylindrical lateral surface of in Fig. 1 illustrated cylinder block 10 (ie, in its circular cylindrical outer surface) formed three each along a circumferential line circumferential grooves, in each of which a sealing ring 20, 22, 24 is received. These sealing rings 20, 22, 24 provide for a seal between the cylinder block 10 and this comprehensive pump housing 14, 16th
  • three mutually identical hollow cylinders 26, 28 are formed, which are each arranged at the same radial distance between the lateral surface of the cylinder block 10 and the cylinder block axis 12. They each have the shape of a straight circular cylinder with parallel to the cylinder block axis hollow cylinder axis 30, 32.
  • Each hollow cylinder 26, 28 is each with respect to the cylinder block axis 12 by 120 degrees offset from the other two hollow cylinders 26, 28 are arranged.
  • the cross-sectional plane passes through the one of these hollow cylinder 26 (the upper in Fig. 1 ).
  • another of these hollow cylinders 28 (the lower in Fig. 1 ), which is offset in the cross-sectional plane (ie offset by 60 degrees with respect to the cylinder block axis 12).
  • the hollow cylinders 26, 28 are each bounded by a first base surface (also referred to as a front base surface) and a circular cylindrical lateral surface.
  • a delivery piston 34, 36 in the direction of the associated hollow cylinder axis 30, 32 slidably disposed such that between the first base of the hollow cylinder 26, 28, one of these facing end side of the delivery piston 34, 36 (as a front end side the delivery piston 34, 36) and a part of the lateral surface of the hollow cylinder 26, 28 a delivery chamber 38, 40 is included for receiving the fuel oil to be delivered.
  • the three each formed by a hollow cylinder 26, 28 and a slidably received therein delivery piston 34, 36 formed piston-cylinder assemblies are identical to each other and arranged with respect to the cylinder block axis 12 rotationally symmetrical to each other.
  • the drive device for an axial piston pump of Fig. 1 shown type is known per se and is therefore described only briefly.
  • the rotating together with the drive shaft 42 swash plate 44 which is arranged in the pump housing 14, 16 outside of the cylinder block 10, thereby cyclically actuates the delivery piston 34, 36 in the axial direction back and forth by against the spring force of return springs 46, 48 on the from the delivery chambers 38, 40 facing away from the longitudinal ends of the delivery piston 34, 36 presses.
  • the delivery pistons 34, 36 are designed as piston rams 50, 52 in the region of these longitudinal ends, which projects out of the cylinder block 10 in the axial direction through the open second base surfaces of the hollow cylinders 26, 28.
  • a drive device based on a swashplate 44 just as well any other suitable drive device for driving the delivery pistons 34, 36 could be used.
  • Fig. 1 the upper delivery piston 34 is shown in its maximum compression position. In this position, with minimal delivery chamber volume 38, it is pushed completely forward in the hollow cylinder 26, so that its front end side is arranged in the immediate vicinity of the front base surface of the hollow cylinder 26.
  • Each piston-cylinder arrangement further comprises one each through the first (front) base surface of the hollow cylinder 26, 28 into the delivery chamber 38, 40 inflowing inflow line 54, 56 and an out of the delivery chamber 38, 40 leading outflow line 58, 60 for that promoting fuel oil.
  • the region of the pump arranged in front of the delivery chamber 38, 40 with respect to the direction of flow of the fuel oil to be delivered is referred to as the low-pressure region or the suction region of the pump.
  • the fuel oil is under a comparatively low pressure, which is between the vapor pressure of the heating oil and the atmospheric pressure in the vicinity of the pump.
  • the in terms of the Flow direction downstream of the pumping chamber 38, 40 arranged pump region is referred to as the high-pressure region of the pump, wherein prevail in this range Schuöldrücke between the atmospheric pressure and about 700 bar.
  • the pressure in the delivery chamber 38, 40 corresponds approximately to the pressure in the suction region.
  • the pressure in the delivery chamber 38, 40 substantially corresponds to the pressure in the high-pressure region of the pump.
  • the discharge lines 58, 60 of all three hollow cylinders 26, 28 open on a common circumferential line on the cylinder jacket-shaped outer surface of the cylinder block 10. They are connected via a high-pressure connecting line 62 with each other and with a arranged in the first pump housing part 14 pressure port 64 in the high pressure region of the pump, wherein this high-pressure connecting line 62 is formed as the aforementioned circumferential line along circumferential groove 62 in the cylinder jacket-shaped outer surface of the cylinder block 10 comprehensive surface of the first pump housing part 14.
  • the inflow lines 54, 56 are connected to the hollow cylinders 26, 28 via low-pressure connecting lines (not shown) with each other and with a suction port 66 arranged in the first pump housing part 14 in the low-pressure region of the pump.
  • the discharge line 58, 60 of each hollow cylinder 26, 28 is a channel in the cylinder block 10 formed on one side of the outer surface of the cylinder block 10 to this hollow cylinder 26, 28.
  • This channel leads from the delivery chamber 38, 40 arranged in the hollow cylinder 26, 28 from a point in the immediate vicinity of the front base of the hollow cylinder 26, 28, straight on the direct and shortest way through the lateral surface of the hollow cylinder 26, 28 therethrough to the outer surface of the cylinder block 10. That is, the channel of the discharge line 58, 60 in the radial Direction both in relation to the axis 30, 32 of the hollow cylinder 26, 28 and with respect to the cylinder block axis 12 from the delivery chamber 38, 40 to the outer surface of the cylinder block 10 extends.
  • the delivery pistons 34, 36 have a circumferential reduction 68, 70 in their foremost region adjoining the front end side.
  • annular channel between the Delivery piston 34, 36 and this comprehensive hollow cylinder 26, 28 created.
  • Fig. 1 recognizable by the example of the upper delivery piston 34, its front end face in front of the mouth of the outflow line 58 is arranged in the delivery chamber 38 in its foremost position.
  • the annular channel is arranged above the mouth of the outflow channel 58, so that even in this position fuel oil can still flow out of the delivery chamber 38 through the outflow channel 58.
  • the suction valves are each provided with a shut-off in the form of a ball 72, 74, which are arranged in the inflow line 54, 56 upstream of the hollow cylinder 26, 28 immediately before the first base.
  • axial piston pump shown differs only in terms of the design of the suction valves of the in Fig. 1 shown axial piston pump and is otherwise identical to the latter formed.
  • This in Fig. 4 illustrated suction valve in the form of a check valve is a conical seat valve. It has a shut-off, which is provided with a flat portion 174 and formed conically on its side facing the valve seat edge.
  • the shut-off body is arranged in the axial direction upstream immediately before the hollow cylinder 28 such that the flat portion 174 forms a part of the boundary wall of the delivery chamber 40 in the closed state of the suction valve. As a result, a particularly small dead volume is achieved.
  • axial piston pump As well as in the case of Fig. 4 axial piston pump shown is in the inflow line 54, 56 upstream of the suction valves immediately before the same one each made of sintered bronze, disc-shaped diffusion element 76, 78 arranged in front of each suction valve. These diffusion elements 76, 78 cause a reduction in the size of any gas bubbles present in the heating oil.
  • each outflow line 58, 60 each serving as a pressure valve check valve in the vicinity of the mouth of the discharge line 58, 60 arranged in the cylinder jacket-shaped outer side of the cylinder block 10.
  • This in Fig. 1 illustrated pressure valve is provided with a valve seat which is formed in a directly adjacent to the outer surface of the cylinder block 10 lot of the channel of the discharge line 58 as a bore in the channel.
  • the cylinder block 10 is arranged in the first pump housing part 14 in such a way that the outer surface of the cylinder block 10 is enclosed by the first pump housing part 14 in the region of the outflow line 58 (ie in the region of the mouth of the discharge line 58 in the outer surface).
  • the pressure valve is provided with a shut-off in the form of a ball 80 which rests on the valve seat and against the spring force of a closing spring 82 in the radial direction of the valve seat (and the cylinder block) is displaced away to open the pressure valve.
  • the valve seat and the ball 80 are formed and arranged such that the ball 80 is arranged even in the closed state of the pressure valve to more than half outside the cylinder jacket-shaped outer surface of the cylinder block 10.
  • the closing spring 82 of the pressure valve is arranged completely outside the cylinder block 10 in the first pump housing part 14. This makes it possible, in the course of a revision of the pump, to replace only the cylinder housing 10 together with the parts arranged therein, while the spherical shut-off body 80 and the closing spring 82 of the pressure valve can be left in the pump housing 14, 16.
  • FIGS. 2 and 3 illustrated axial piston pumps which relate to two embodiments of the invention, differ only in terms of the design of the pressure valves of the in Fig. 1 shown axial piston pump and are otherwise identical to the latter formed.
  • a circumferential groove 284 is formed, which extends along the circumferential line on which the outflow lines 58, 60 of the three hollow cylinders 26, 28 open.
  • This in Fig. 2 Pressure valve shown by way of example is provided with a valve seat which, as a bore 286 leading from the outer surface of the cylinder block 10 through the groove 284, into the channel of the discharge line 58 is trained.
  • the bore 286 is dimensioned such that it can accommodate a serving as a shut-off ball 280 completely such that it is disposed radially within the circumferential groove 284 in the cylinder block 10.
  • this groove 284 made of nitrile rubber O-ring 282 is arranged such that it presses on the balls 280 of all three along the groove 284, mutually identical pressure valves radially inwardly and thereby acts as a common closing spring for these pressure valves.
  • Fig. 3 illustrated pressure valve differs from that in Fig. 2 shown pressure valve only in that the circumferential groove 384 is formed slightly wider and neither balls as shut-off nor holes are provided as valve seats for such balls. Instead, the nitrile rubber O-ring 380 disposed in the circumferential groove 384 is configured and arranged to simultaneously act as both a shut-off and closing element for all three pressure valves.
  • the invention provides an axial piston pump which has a simple construction and a comparatively small dead volume between the suction valve and the pressure valve.

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  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
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  • Reciprocating Pumps (AREA)

Claims (8)

  1. Pompe à pistons axiaux destinée à l'alimentation en un fluide, comprenant un bloc-cylindres (10) qui présente une surface extérieure qui a au moins en partie la forme d'une surface périphérique d'un cylindre, au moins un cylindre creux (26, 28) conçu dans le bloc-cylindres (10), un piston d'alimentation (34, 36) agencé dans le cylindre creux (26, 28) de manière coulissante, une chambre d'alimentation (38, 40) étant comprise entre les parois du cylindre creux (26, 28) et un côté frontal du piston d'alimentation (34, 36) afin de recevoir le fluide d'alimentation, une conduite d'écoulement (58, 60) sortant de la chambre d'alimentation (38, 40), qui est conçue sous forme de canal dans le bloc-cylindres (10) et qui conduit le fluide de la chambre d'alimentation (38, 40) à au moins une partie en forme de corps de cylindre de la surface extérieure du bloc-cylindres (10), et au moins une soupape de retenue servant de soupape de refoulement, dont le siège de soupape est agencé dans une partie du canal de la conduite d'écoulement (58, 60) directement adjacente à la partie en forme de corps de cylindre de la surface extérieure du bloc-cylindres (10), caractérisée en ce que un élément à ressort de fermeture (282, 380) est réalisé à partir d'un matériau élastique, et en ce que l'élément à ressort de fermeture (282, 380) présente une forme annulaire ou une forme de C et s'étend le long d'une ligne périphérique de la partie en forme de corps de cylindre de la surface extérieure du bloc-cylindres (10), étant agencé de manière à agir comme un ressort de fermeture pour la soupape de refoulement.
  2. Pompe à pistons axiaux selon la revendication 1, caractérisée en ce qu'une rainure circonférentielle (284, 384) est réalisée le long de la ligne périphérique de la partie en forme de corps de cylindre de la surface extérieure du bloc-cylindres (10), afin de loger l'élément à ressort de fermeture (282, 380), la conduite d'écoulement (58, 60) débouchant dans la rainure (284, 384).
  3. Pompe à pistons axiaux selon la revendication 2, caractérisée en ce que le siège de soupape de la soupape de refoulement est conçu comme un alésage (286) conduisant depuis la surface extérieure du bloc-cylindres (10) à travers la rainure (284) dans le canal de la conduite d'écoulement (58), l'alésage (286) étant mesuré de manière à pouvoir recevoir entièrement une bille (280) servant de corps de blocage, de sorte qu'elle soit disposée dans la rainure circonférentielle (284) du bloc-cylindres, et qu'elle soit pressée radialement vers l'intérieur par l'élément à ressort de fermeture (282).
  4. Pompe à pistons axiaux selon la revendication 1 ou 2, caractérisée en ce que l'élément à ressort de compression (380) est configuré et disposé de telle sorte qu'il agisse en même temps comme un corps de blocage (380) de la soupape de refoulement ou des soupapes de refoulement, pour lesquels il sert d'élément à ressort de fermeture (380).
  5. Pompe à pistons axiaux selon l'une quelconque des revendications 1 à 4, caractérisée en ce qu'elle présente au moins deux soupapes de refoulement, qui sont conçues et disposées de telle sorte que l'élément à ressort de fermeture (282, 380) agisse comme un ressort de fermeture commun au moins pour les deux soupapes de refoulement.
  6. Pompe à pistons axiaux selon l'une quelconque des revendications 1 à 5, caractérisée en ce que le canal de la conduite d'écoulement (58, 60) est formé de manière à conduire le fluide sur le court chemin allant du cylindre creux (26, 28) à la surface extérieure du bloc-cylindres (10).
  7. Pompe à pistons axiaux selon l'une quelconque des revendications 1 à 6, caractérisée en ce que le bloc-cylindres (10) est agencé de manière sélectivement échangeable dans un carter de pompe (14, 16) comprenant au moins partiellement ce dernier, de telle sorte que la surface extérieure du bloc-cylindres (10) soit enfermée dans la zone de la conduite d'écoulement (58, 60) du carter de pompe (14, 16).
  8. Pompe à pistons axiaux selon l'une quelconque des revendications 1 à 7, caractérisée en ce que le bloc-cylindres (10) est une pièce moulée monobloc.
EP06015437A 2002-07-05 2002-07-05 Pompe hydraulique à pistons axiaux Expired - Lifetime EP1715183B1 (fr)

Priority Applications (3)

Application Number Priority Date Filing Date Title
AT06015437T ATE403804T1 (de) 2002-07-05 2002-07-05 Hydraulische axialkolbenpumpe
EP06015437A EP1715183B1 (fr) 2002-07-05 2002-07-05 Pompe hydraulique à pistons axiaux
DE50212619T DE50212619D1 (de) 2002-07-05 2002-07-05 Hydraulische Axialkolbenpumpe

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
EP02405569A EP1378662A1 (fr) 2002-07-05 2002-07-05 Pompe hydraulique à pistons axiaux
EP06015437A EP1715183B1 (fr) 2002-07-05 2002-07-05 Pompe hydraulique à pistons axiaux

Related Parent Applications (1)

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EP02405569A Division EP1378662A1 (fr) 2002-07-05 2002-07-05 Pompe hydraulique à pistons axiaux

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EP1715183A2 EP1715183A2 (fr) 2006-10-25
EP1715183A3 EP1715183A3 (fr) 2006-12-20
EP1715183B1 true EP1715183B1 (fr) 2008-08-06

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EP02405569A Withdrawn EP1378662A1 (fr) 2002-07-05 2002-07-05 Pompe hydraulique à pistons axiaux
EP06015437A Expired - Lifetime EP1715183B1 (fr) 2002-07-05 2002-07-05 Pompe hydraulique à pistons axiaux

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR20090058475A (ko) 2006-09-18 2009-06-09 로베르트 보쉬 게엠베하 유체정역학적 기계용 밸브 장치
CN104595286A (zh) * 2015-01-31 2015-05-06 南通恒力重工机械有限公司 一种放油彻底的液压机
CN107013522B (zh) * 2017-05-09 2018-09-25 太原科技大学 配流副的压紧力调节装置
CN106930995B (zh) * 2017-05-09 2018-09-25 太原科技大学 一种柱塞式液压元件的压紧力调节装置
IT201900020050A1 (it) * 2019-10-30 2021-04-30 Annovi Reverberi Spa Valvola bidirezionale automatica e pompa dotata di detta valvola
DE102021125838A1 (de) * 2021-10-05 2023-04-06 Solo Kleinmotoren Gmbh Kolben-Hochdruckpumpe mit kleinem Fördervolumen

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE707462C (de) * 1938-12-02 1941-06-23 Rudolf Mueller Kolbenpumpe mit in einer Zylindertrommel im Kreise angeordneten parallelen Kolben
US2672819A (en) * 1948-12-31 1954-03-23 Schweizerische Lokomotiv Expansible-chamber and positivedisplacement type pump of variable capacity
FR1587661A (fr) * 1968-08-02 1970-03-27
DE1951234B2 (de) * 1969-10-10 1974-07-11 Linde Ag, 6200 Wiesbaden Axialkolbenmaschine für ein hydrostatisches Ferngetriebe
US3832094A (en) * 1973-03-23 1974-08-27 Int Basic Economy Corp Hydraulic pump
DE3723988A1 (de) * 1987-07-20 1989-02-09 Hydromatik Gmbh Axialkolbenmaschine, deren kolben als stufenkolben ausgebildet sind

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Publication number Publication date
EP1378662A1 (fr) 2004-01-07
EP1715183A3 (fr) 2006-12-20
EP1715183A2 (fr) 2006-10-25

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