EP0021315B1 - Machine à piston, notamment pompe à piston - Google Patents

Machine à piston, notamment pompe à piston Download PDF

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Publication number
EP0021315B1
EP0021315B1 EP80103359A EP80103359A EP0021315B1 EP 0021315 B1 EP0021315 B1 EP 0021315B1 EP 80103359 A EP80103359 A EP 80103359A EP 80103359 A EP80103359 A EP 80103359A EP 0021315 B1 EP0021315 B1 EP 0021315B1
Authority
EP
European Patent Office
Prior art keywords
piston
lubricant
collecting chamber
pump
supply
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
Application number
EP80103359A
Other languages
German (de)
English (en)
Other versions
EP0021315A1 (fr
Inventor
Bernhard Frey
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.)
Hydrowatt Systems Ltd
Original Assignee
Hydrowatt Systems Ltd
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 Hydrowatt Systems Ltd filed Critical Hydrowatt Systems Ltd
Priority to AT80103359T priority Critical patent/ATE14915T1/de
Publication of EP0021315A1 publication Critical patent/EP0021315A1/fr
Application granted granted Critical
Publication of EP0021315B1 publication Critical patent/EP0021315B1/fr
Expired legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01M—LUBRICATING OF MACHINES OR ENGINES IN GENERAL; LUBRICATING INTERNAL COMBUSTION ENGINES; CRANKCASE VENTILATING
    • F01M1/00—Pressure lubrication
    • F01M1/02—Pressure lubrication using lubricating pumps
    • 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
    • F04B1/0408—Pistons
    • 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
    • F04B1/0439—Supporting or guiding means for the pistons
    • 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
    • F04B43/00—Machines, pumps, or pumping installations having flexible working members
    • F04B43/08—Machines, pumps, or pumping installations having flexible working members having tubular flexible members
    • F04B43/084—Machines, pumps, or pumping installations having flexible working members having tubular flexible members the tubular member being deformed by stretching or distortion

Definitions

  • the invention relates to a piston machine according to the preamble of claim 1, in particular a piston pump.
  • a piston machine is known from DE-A-2 554 733.
  • the object of the invention is therefore to provide a piston machine of the type mentioned at the outset, which is distinguished by a high level of operational reliability of the lubrication system and which secures the sensitive sealing member against damage by dry or mixed friction on the support surface.
  • the solution to this problem according to the invention is characterized by the features of claim 1. This solution advantageously enables a safe filling of the lubricant return device or return pump without foam formation on the one hand and without risk of flooding on the other hand.
  • the drive device 10 of the pump according to FIG. 1 consists of a shaft 1 with an eccentric 2 coupled to a motor (not shown), on which a non-rotating, translationally rotating sliding piece 3 with a number of cylinders - here for example five - corresponding to the number of tangential pressure surfaces 4 is mounted .
  • a pressure surface is indicated in operative connection with a drive member 30 of a piston 20 which is connected to an elastically deformable sealing hose 22.
  • a coil spring 23 presses the piston 20 against the bottom portion 30b of the sleeve-shaped drive member 30 and sets the sealing hose under axial tension.
  • the sealing hose sits in the bore of a cylinder 25, with which it is firmly connected at the upper end, and thus hermetically seals the working space 24 formed in the hose interior.
  • This working space changes its volume in accordance with the oscillating movement of the drive member 30 and generates the pumping action in connection with check valves 26 and 27 which are connected to a delivery and suction channel 28.
  • the lubrication system of the pump is in the form of pressure circulation lubrication with a gear pressure lubrication pump 100, a return collecting space 120 surrounding the eccentric 2 of the drive device and with an annular storage space 110 concentrically surrounding the axis of rotation XX of the drive device and with one from the return collecting space 120 into the Storage pump 110 promoting return pump 105 is formed.
  • This design and arrangement of the storage space enables a particularly space-saving multi-cylinder pump construction with a symmetrical distribution of the connections to the individual cylinders over the circumference of the ring.
  • the inclusion of the storage space in the cylindrical housing of the star-shaped multi-cylinder arrangement also serves the same purpose.
  • the pressure lubrication pump 100 delivers from the storage space 110 via channels 103 and 104 and a filter 102 into an annular distributor channel 101, from where pressure channels 90 and 95 lead to the individual cylinders 25 with adjusting throttles 90a and 95a.
  • the pressurized lubricant from the channel 90 is supplied to support the sliding movement of the outer surface of the sealing hose 22 and flows in the axial direction of the cylinder (downwards according to FIG. 1) into a pulsating space 42 formed in the area of the lower piston and cylinder end .
  • This space stands over a throttle duct 45, which is designed as a gap between the inner surface of the cylindrical section 30a of the drive member 30 and the outside of the cylinder 25, with one at the upper end of the cylindrical section 30a formed, also pulsating secondary space 35 in connection.
  • the relaxed lubricant flowing out in the space 42 is conveyed into the adjoining space 35 via the throttle channel 45 acting as a quasi check valve, so that the space 42 essentially acts as a low-pressure space for an undisturbed outflow of the lubricant from the gap between the sealing hose and the cylinder bore or support surface acts.
  • low pressure is also required in the adjoining room 35.
  • the latter is connected to the storage space 110 via a compensation channel 40 with a large cross section, which thus serves as a pressure compensation space.
  • the lubricant supplied via the channel 95 reaches the outer surface of the cylindrical section 30a of the drive member 30, where the latter is guided so as to be displaceable coaxially with the cylinder 25.
  • the lubricant then flows via lubrication channels 47 to the pressure surfaces 4 and further into the return collecting space 120. This lubricant circuit is also closed.
  • the return pump 105 draws in from the lower part of the collecting space 120 via a channel 115 and delivers via an ascending return channel 106 in the apex region 110a of the storage space 110. This results in an effective ventilation of the lubricant flow entering the storage space.
  • the suction space of the latter i.e. the lower part of the collecting space 120
  • overflow channel 130 connecting the storage space 110, which prevents this space from being sucked empty.
  • An actuator is provided for limiting the overflow, for which an adjustable throttle 135a may be sufficient, for example.
  • an overflow control with a controllable valve 135 as an actuator and with a float 140 as a control device is provided. This allows an optimal filling level to be maintained in the suction space of the return pump 105. Sufficient filling of the return pump is essential, in particular, to avoid foaming, which would impair reliable pressure circulation lubrication.
  • FIG. 2 The pressure circulation lubrication system of the pump is shown schematically in a clear form in FIG. 2, the essential functional elements being shown symbolically, but with the same reference numerals as in FIG. 1.
  • the avoidance of foam formation in the delivery system of the circulating pressure lubrication is essential for a perfect function.
  • the design of the rotor 105a of the return pump 105 shown in FIGS. 4 and 4 serves in particular with a plurality of slots designed as storage spaces 105b, which are arranged in the manner of a radial centrifugal pump and extend over a radius difference with respect to the axis of rotation XX of the pump.
  • the lubricant located in these storage spaces is subject to a separation between lubricants with a greater or lesser liquid content or, conversely, a lower and greater gas or foam content.
  • the stowage spaces then connect to an outflow control opening 109b which receives the gas or foam-rich part of the lubricant and leads back into the collecting space 120 via an outflow channel 109c, which is not shown in detail.
  • the outflow control openings 108 and 109b which, as shown in FIG. 3, likewise extend over an angle of substantially less than 180 °, the storage spaces 105b are closed at their outer ends by a housing inner surface 107, so that this Part of the circulation is available for separating the differently dense lubricant components without disturbance due to flow.
  • FIG. 4 Another mechanism that contributes to gas and foam cut-off within the rotor of the return pump is indicated in FIG. 4. Thereafter, a radial circular flow with a course indicated at A can be generated by means of a comparatively wide gap space 109a arranged axially next to the rotor 105, which is shown here in a strongly distorting manner, which prevents the accumulation of the low-gas lubricant in the radially outer regions of the storage spaces 105b favored and possibly also a partial return of the foam accumulated in the radially inner storage space areas in the direction of the suction chamber of the pump.
  • a cooling device for the lubricant is accommodated within the annular lubricant storage space 110.
  • This cooling device essentially consists of a heat exchanger 210 which has a channel system 212 through which the working medium of the pump flows and which can be seen in detail in FIG. 6.
  • the flow of the working medium in this channel system is achieved by means of the feed pump 150 already mentioned, which is accommodated coaxially to the annular storage space 110 and with an axial overlap in its inner recess space 240.
  • the inflow side 160 of the prefeed pump 150 lies in the area of an axial end cover 155 of the pump housing, which is aligned with an end wall 230 closing off the storage space 110.
  • the pre-feed pump is designed as an axial flow pump, the rotor of which is seated on the pump shaft 1 in the manner shown schematically in FIG. 5 and the outflow side 170 of which is connected to an annular channel 174 by radial channels 172. From the latter, axial branch ducts 176 (only one of these ducts is shown in FIG. 5) lead to the individual, pump-shaped pump cylinders (not shown in detail).
  • the piston-cylinder arrangements of the pump receive the working fluid with a pre-pressure of, for example, a few bar overpressure, which is sufficient for a safe filling in the suction stroke of the pistons.
  • Channel sections 178 which are lengthened at the rear connect the outflow side 170 of the pre-feed pump 150 to an annular channel 180 in a central, section-like section 232 of the end wall 230.
  • a radial channel 182 leads to an inflow distributor 216 of the heat exchanger which is inserted in the outer part of the end wall 230 210.
  • the inflow distributor arranged in the lower apex area of the storage space 110 From this inflow distributor arranged in the lower apex area of the storage space 110, the partial flow of the cool working medium branched off from the outflow side of the pre-feed pump passes via a channel system 212 of the heat exchanger 210, which can be seen in detail in FIG.
  • Outflow collector 218 arranged diametrically to the inflow distributor 216.
  • the latter is also inserted into the outer part of the end wall 230.
  • the outflow collector is connected to the suction side 160 of the prefeed pump via a radial channel 184. This results in a return flow circuit parallel to the main delivery flow for the branched-off part of the delivery flow of the prefeed pump 150, which is fed to the inflow side of the main pump.
  • a throttle screw 220 is inserted into the end wall 230, the tip of which engages in the channel 182 and here forms an adjustable throttle point in the partial feed flow to the inflow distributor 216.
  • the design of the heat exchanger is shown in detail in Fig. 6.
  • the channel system 212 of the heat exchanger is then practically completely submerged within the lubricant storage space 110 and below the lubricant level.
  • the return flow channel 106 from the lubricant return pump 105 in the upper part of the crown 110a of the storage space 110 and the suction by the pressure lubrication pump 100 in the lower part of the crown, there is a lubricant flow in the annular storage space which essentially goes down in both circumferential directions from the top of the crown lower apex runs.
  • the channel system 212 of the heat exchanger 210 comprises a plurality of ring-shaped heat exchanger tubes 214 which extend in the circumferential direction of the storage space 110 and which, as mentioned, essentially below the lubricant level and therefore enable heat exchange over their entire surface.
  • a plurality of heat exchanger tubes 214 connected in parallel, arcuate and adapted to the ring shape of the storage space 110 are connected.
  • the result is an essentially cylindrical arrangement of heat exchanger tubes lying side by side in the cylinder axis direction, i.e. a large-scale arrangement of heat transfer surfaces adapted to the spatial conditions of the storage room and the lubricant flow.

Claims (19)

1. Machine à piston avec au moins un ensemble cylindre et piston pour la formation d'un espace vibratoire de travail, avec un mécanisme de commande (10) pour la production d'un mouvement relatif oscillant entre le piston (20) et le cylindre (25), avec un système de lubrification pour l'ensemble cylindre et piston et avec un organe d'étanchéité déformable, élastiquement mou, servant à l'étanchéification de l'espace de travail, qui s'appuie, par intermédiaire d'un lubrifiant, sur une surface d'appui, de manière glissante, caractérisée en ce que le système de lubrification est configuré comme une lubrification continue sous pression avec une pompe de lubrification sous pression (100) pour l'alimentation en lubrifiant de l'ensemble cylindrique et piston, avec un espace de réserve (110) alimentant la pompe de lubrification sous pression (100), avec un collecteur de retour (120) disposé, dans la direction du passage du lubrifiant, après l'ensemble cylindre et piston et avec un système de retour du lubrifiant (105), en ce qu'un dispositif est prévu coopérant avec le collecteur de retour (120), pour le maintien d'une quantité minimum de lubrifiant dans le collecteur de retour (120) et en ce que le dispositif de retour du lubrifiant (105) est raccordé entre le collecteur de retour (120) et l'espace de réserve (110).
2. Machine à piston selon la revendication 1 caractérisée par un canal de débordement (130) reliant l'espace de réserve (110) au collecteur de retour (120).
3. Machine à piston selon la revendication 2 caractérisée par un canal de débordement (130) avec un organe de réglage (135) pouvant être ajusté ou commandé, pour une limitation de l'écoulement de l'espace de réserve (110) au collecteur de retour (120).
4. Machine à piston selon la revendication 3 caractérisée en ce que pour le collecteur de retour (120), un système de régulation ou de commande (140) coopère avec l'organe de réglage de l'écoulement (135) dans le canal de débordement (130).
5. Machine à piston selon l'une quelconque des revendications précédentes caractérisée en ce que l'espace de réserve (110) est de forme annulaire et entourant l'axe de rotation XX d'un mécanisme rotatif de commande (10) et avantageusement concentriquement.
6. Machine à piston selon la revendication 5 caractérisée en ce que le plan annulaire de l'espace de réserve ou collecteur (110) est disposé essentiellement verticalement et en ce qu'un canal de retour (106) raccordé à une pompe de retour (105) est prévu, qui débouche dans la zone de sommet (110a) de l'espace annulaire de réserve ou collecteur (110).
7. Machine à piston selon la revendication 6 caractérisée par une disposition polycylindrique en étoile avec un espace de réserve ou collecteur (110) en forme de couronne, qui est disposé côté frontal et coaxialement à la disposition polycylindrique en étoile dans un carter commun.
8. Machine à piston selon l'une quelconque des revendications précédentes caractérisée en ce qu'un système (200) de refroidissement du lubrifiant est prévu, ayant au moins un échangeur de chaleur (210) sollicité par le fluide de travail de la machine à piston, qui sert de fluide de refroidissement.
9. Machine à piston selon la revendication 8 caractérisée en ce que l'échangeur de chaleur (210) est disposé dans la zone de l'espace de réserve ou collecteur (110) du lubrifiant.
10. Machine à piston selon la revendication 9 caractérisée en ce que l'échangeur de chaleur (210) est configuré comme un système de canaux (212) traversé par le fluide de travail et est disposé à l'intérieur de l'espace de réserve ou collecteur du lubrifiant (110).
11. Machine à piston selon l'une quelconque des revendications 5 à 10 caractérisée en ce que le système de canaux (212) de l'échangeur de chaleur (210) présente un certain nombre de tubes d'échangeur de chaleur (214) de forme annulaire, s'étendant dans la direction périphérique de l'espace (110) de réserve ou collecteur du lubrifiant, dont les surfaces externes sont au moins partiellement en contact avec le lubrifiant.
12. Machine à piston selon la revendication 11 caractérisée en ce que le système de canaux (212) de l'échangeur de chaleur (210) présente au moins deux raccordements disposés avantageusement diamétralement l'un à l'autre dans l'espace annulaire de réserve ou collecteur du lubrifiant 110, dont l'un est configuré comme diviseur d'afflux (216) et dont l'autre comme collecteur d'écoulement (218), et en ce qu'à chaque fois un certain nombre de tubes (214) d'échangeur de chaleur parallèles les uns aux autres passent, en forme d'arc, dans les deux directions périphériques, du diviseur d'afflux (216) au collecteur d'écoulement (218).
13. Machine à piston selon la revendication 12 caractérisée en ce que les tubes d'échangeur de chaleur (214) en forme d'arc en direction périphérique de l'espace de réserve ou collecteur (110) forment une disposition essentiellement cylindrique de tubes adjacents dans la direction de l'axe du cylindre.
14. Machine à piston selon l'une quelconque des revendications 10 à 13 caractérisée en ce que le passage du fluide de travail dans l'espace de réserve ou collecteur (110) d'une part et l'écoulement du lubrifiant dans l'échangeur de chaleur (210) d'autre part se produisent au moins par segment, mutuellement à contre-courant.
15. Pompe à piston selon l'une des revendications 9 à 14 caractérisée en ce qu'une pompe de pré-alimentation (150) est prévue, amenant le fluide de travail au côté afflux de la pompe, et en ce que le côté afflux du fluide de travail de l'échangeur de chaleur (210) est raccordé au côté écoulement (170) de la pompe de pré-alimentation (150).
16. Pompe à piston selon la revendication 15 caractérisée en ce que le système du fluide de travail de l'échangeur de chaleur (210) est configuré comme une ramification entre le côté écoulement (170) et le côté afflux (160) de la pompe de pré-alimentation (150).
17. Pompe à piston selon la revendication 16 caractérisée en ce que dans la ramification de l'échangeur de chaleur est disposé au moins un étranglement (220) réglable.
18. Pompe à piston selon les revendications 11 à 15 caractérisée en ce que l'espace de réserve ou collecteur du lubrifiant (110) de forme annulaire est disposé au moins presque coaxialement à la pompe de pré-alimentation (150) avantageusement configurée comme machine à écoulement axial et de manière à la recouvrir au moins partiellement axialement.
19. Pompe à piston selon l'une quelconque des revendications 12,16 et 18 caractérisée en ce que le diviseur d'afflux (216) et le collecteur d'écoulement (218) sont disposés dans une paroi frontale axiale (230) de l'espace de réserve ou collecteur (110) du lubrifiant et sont reliés par des canaux parcourant cette paroi frontale, au côté d'afflux ou respectivement d'écoulement de la pompe de pré-alimentation (150).
EP80103359A 1979-06-20 1980-06-17 Machine à piston, notamment pompe à piston Expired EP0021315B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT80103359T ATE14915T1 (de) 1979-06-20 1980-06-17 Kolbenmaschine, insbesondere kolbenpumpe.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CH577979A CH645435A5 (de) 1979-06-20 1979-06-20 Kolbenpumpe.
CH5779/79 1979-06-20

Related Child Applications (1)

Application Number Title Priority Date Filing Date
EP84108027.8 Division-Into 1984-07-09

Publications (2)

Publication Number Publication Date
EP0021315A1 EP0021315A1 (fr) 1981-01-07
EP0021315B1 true EP0021315B1 (fr) 1985-08-14

Family

ID=4299196

Family Applications (2)

Application Number Title Priority Date Filing Date
EP80103359A Expired EP0021315B1 (fr) 1979-06-20 1980-06-17 Machine à piston, notamment pompe à piston
EP84108027A Expired - Lifetime EP0153982B1 (fr) 1979-06-20 1980-06-17 Machine à piston, particulièrement pompe à piston

Family Applications After (1)

Application Number Title Priority Date Filing Date
EP84108027A Expired - Lifetime EP0153982B1 (fr) 1979-06-20 1980-06-17 Machine à piston, particulièrement pompe à piston

Country Status (16)

Country Link
US (1) US4671743A (fr)
EP (2) EP0021315B1 (fr)
JP (2) JPS5627086A (fr)
AR (1) AR219466A1 (fr)
AT (2) ATE51683T1 (fr)
AU (1) AU5935080A (fr)
BR (1) BR8003711A (fr)
CA (1) CA1142030A (fr)
CH (1) CH645435A5 (fr)
CS (1) CS229656B2 (fr)
DD (1) DD151487A5 (fr)
DE (2) DE3072177D1 (fr)
HU (1) HU183151B (fr)
PL (1) PL130376B1 (fr)
SU (1) SU1380617A3 (fr)
ZA (1) ZA803580B (fr)

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Also Published As

Publication number Publication date
CH645435A5 (de) 1984-09-28
EP0153982B1 (fr) 1990-04-04
BR8003711A (pt) 1981-01-13
ZA803580B (en) 1981-07-29
PL225024A1 (fr) 1981-04-24
JPH0250358B2 (fr) 1990-11-02
US4671743A (en) 1987-06-09
PL130376B1 (en) 1984-08-31
DD151487A5 (de) 1981-10-21
AR219466A1 (es) 1980-08-15
EP0021315A1 (fr) 1981-01-07
CS229656B2 (en) 1984-06-18
ATE51683T1 (de) 1990-04-15
AU5935080A (en) 1981-01-08
DE3070978D1 (en) 1985-09-19
DE3072177D1 (de) 1990-05-10
EP0153982A2 (fr) 1985-09-11
CA1142030A (fr) 1983-03-01
JPS6426096A (en) 1989-01-27
SU1380617A3 (ru) 1988-03-07
JPS6365830B2 (fr) 1988-12-16
EP0153982A3 (en) 1985-11-21
ATE14915T1 (de) 1985-08-15
HU183151B (en) 1984-04-28
JPS5627086A (en) 1981-03-16

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