EP2728190A1 - Hydraulische Kolbenpumpe - Google Patents

Hydraulische Kolbenpumpe Download PDF

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Publication number
EP2728190A1
EP2728190A1 EP13175582.9A EP13175582A EP2728190A1 EP 2728190 A1 EP2728190 A1 EP 2728190A1 EP 13175582 A EP13175582 A EP 13175582A EP 2728190 A1 EP2728190 A1 EP 2728190A1
Authority
EP
European Patent Office
Prior art keywords
bushing
cylindrical
pump
head
annular seal
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
EP13175582.9A
Other languages
English (en)
French (fr)
Other versions
EP2728190B1 (de
EP2728190B8 (de
Inventor
Fulvio Montipo'
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.)
Interpump Group SpA
Original Assignee
Interpump Engineering SRL
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 Interpump Engineering SRL filed Critical Interpump Engineering SRL
Publication of EP2728190A1 publication Critical patent/EP2728190A1/de
Publication of EP2728190B1 publication Critical patent/EP2728190B1/de
Application granted granted Critical
Publication of EP2728190B8 publication Critical patent/EP2728190B8/de
Active legal-status Critical Current
Anticipated expiration legal-status Critical

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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
    • F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
    • F04B53/007—Cylinder heads
    • 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
    • F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
    • F04B53/16—Casings; Cylinders; Cylinder liners or heads; Fluid connections
    • 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
    • F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
    • F04B53/22—Arrangements for enabling ready assembly or disassembly

Definitions

  • the present invention relates to a hydraulic piston pump, in particular a high-pressure hydraulic piston pump for industrial applications.
  • a hydraulic piston pump generally comprises a casing in which a drive shaft is rotatably supported, which drive shaft is able to activate at least a crank mechanism of the con-rod-shaft type giving a respective piston an alternating motion.
  • a head is fixed to the casing, internally of which a blind cylindrical seating is fashioned in which the piston is slidably housed, such as to define a variable-volume pump chamber. Also housed in the cylindrical seating is at least an annular seal, which is suitable for inserting substantially snugly on the piston skirt, such as to delimit and sealingly close the pump chamber.
  • the pump chamber is also delimited by an aspirating valve and a delivery valve, by means of which the chamber can be placed in communication respectively with an aspirating conduit and a delivery conduit that are both fashioned in the head.
  • the fluid to be pumped is aspirated at low pressure through the aspirating valve, is compressed internally of the pump chamber, and lastly is made to exit at high pressure through the delivery valve.
  • a drawback of these hydraulic pumps consists in the fact that each time it is necessary to replace the seal gaskets the hydraulic pump operation has to be halted, the delivery and aspiration conduits evacuated, the connections with the hydraulic circuit in which the hydraulic pump is inserted disconnected, and lastly the head of the casing removed and the pistons extracted.
  • the cylindrical piston seatings are defined by a plurality of cylindrical bushings removably associated to the head, and extractable in the sliding direction of the pistons from the opposite side with respect to the casing.
  • the cylindrical bushings are all associated to a single support plate, which is fixed to the front part of the head by means of a plurality of screws. By removing the screws, the support plate can be distanced from the head, extracting the cylindrical bushings from the respective pistons together with the gaskets.
  • cylindrical bushing extracting operation can be rather tricky, as it can require considerable effort on the part of the operator to overcome the adhesion force that the worn gaskets exert against the walls and against the piston skirt.
  • An aim of the present invention is to obviate the above-mentioned drawbacks in the prior art, with a solution that is simple, rational and relatively inexpensive.
  • the invention discloses a hydraulic piston pump comprising a head in which an aspiration conduit, a delivery conduit, and at least a pump chamber in which an alternating piston is partially housed are fashioned, wherein the pump chamber is separated from the aspirating conduit and from the delivery conduit respectively by an automatic aspirating valve and an automatic delivery valve, which are housed in respective seatings realised in the head, and wherein the piston is slidably housed internally of a cylindrical bushing, which is housed internally of the head and bears at least a first annular seal able to be coaxially interposed between the piston and the bushing, such as to sealingly close the pump chamber.
  • the pump further comprises a cap which is coupled to the bushing by connecting means which constrain the bushing to the cap in an axial direction and enable reciprocal free rotations about the axis of the bushing, the cap being rotatably coupled to the head by threaded means which define a screw axis of the cap coinciding with the axis of the bushing.
  • the cap is further only associated to the respective bushing, so it is possible to proceed to mounting a single bushing at a time, leaving the ones having still-efficient seals in their housings.
  • the connecting means between the bushing and the cap can comprise a plurality of axial tabs projecting from a first end of the cylindrical bushing and arranged circumferentially about the axis of the bushing, angularly distanced from one another, which tabs snap-fit to a cylindrical shank realised at an end of the cap.
  • the engaging tabs facilitate the operations of mounting and demounting the bushing from the cap.
  • the cylindrical bushing (30) further bears a second annular seal (low-pressure) able to be coaxially interposed between the piston and the bushing, which is positioned at a certain axial distance from the first annular seal (high pressure).
  • a second annular seal low-pressure
  • the second annular seal prevents small quantities of fluid, possibly leaking from the first seal, from exiting the pump.
  • the lateral wall of the cylindrical bushing can be provided with at least a discharge through-hole, which is interposed between the first and second annular seal and is in communication with the aspirating conduit via a scavenger conduit afforded in the head.
  • the cylindrical bushing bears a third annular seal (high-pressure) able to be coaxially interposed between the cylindrical bushing and a relative cylindrical seating of the head in which the bushing is housed.
  • the advantage of this solution is to prevent the fluid to be pumped from exiting from the pump chamber by leaking between the cylindrical bushing and the respective housing seating of the head.
  • the cylindrical bushing can also bear a fourth annular seal (low pressure) able to be coaxially interposed between the cylindrical bushing and the relative cylindrical seating, which is positioned such that the discharge hole (for recycling the leakage) is also located between the third and fourth annular seal.
  • a fourth annular seal low pressure
  • the cylindrical bushing comprises a first cylindrical portion and a second cylindrical portion which are coaxial and reciprocally coupled by means of further connecting means able to constrain them reciprocally at least in an axial direction, for example using further snap-fit means.
  • This solution has the advantage of providing a cylindrical bushing which is separable into two easily-demountable and re-mountable components, thus simplifying the replacement of the various seals associated to the bushing.
  • the second cylindrical portion is at least partly inserted internally of the first cylindrical portion, such that the first annular seal (high-pressure between the piston and the bushing)is axially interposed and blocked between the second cylindrical portion and an abutment of the first cylindrical portion.
  • the second annular seal (low-pressure between the piston and the bushing) is borne by the second cylindrical portion of the bushing
  • the third seal high-pressure between the bushing and the head
  • the fourth annular seal (low-pressure between the bushing and the head) is borne by the second cylindrical portion of the bushing.
  • the cylindrical bushing is at least partly made of a plastic material, for example only the first cylindrical portion, only the second cylindrical portion, or both.
  • 21 denotes in its entirety a hydraulic piston pump comprising a head 10 (i.e. an external body) in which the following are fashioned: an aspirating conduit 12, a delivery conduit 13 and at least a pump chamber 11, which communicates with the aspiration conduit 12 and delivery conduit 13 via corresponding aspiration and delivery valves 121 and 131.
  • a head 10 i.e. an external body
  • the following are fashioned: an aspirating conduit 12, a delivery conduit 13 and at least a pump chamber 11, which communicates with the aspiration conduit 12 and delivery conduit 13 via corresponding aspiration and delivery valves 121 and 131.
  • valves 121 and 131 are housed in special seatings fashioned in the head 10 and fixed thereto with the aid of relative caps 122 and 132 screwed to the head 10.
  • the valves 121 and 131 are automatic valves of known type and are therefore not described in further detail.
  • An alternating piston 14 is partially housed in the pump chamber 11, which piston 14 is pivoted to a thrust mechanism 20 activated by a motor (not shown in the figures) and contained in a casing 21 fixed to the head 10.
  • the piston 14 is coaxially housed internally of a substantially cylindrical bushing 30, in such a way as to be slidable alternatingly in the direction defined by the longitudinal axis A of the bushing 30.
  • the bushing 30 is in turn housed in a cylindrical seating 16 afforded internally of the head 10, so that the internal volume of the bushing 30 is able to at least partially define the pump chamber 11.
  • the bushing 30 is coaxially coupled to a cap 31, which can be removably fixed to the head 10.
  • the cap 31 comprises a cylindrical shank 311, the external lateral surface of which is provided with a thread.
  • the cap 31 is screwed via the thread to an opening afforded in the head 10 in the opposite side to the casing 21, such as to obstruct it.
  • the screwing/unscrewing axis of the cap 31 coincides with the longitudinal axis of the bushing 30, which is coupled to the cap 31 by connecting means which constrain it in the axial direction but allow free rotations about the longitudinal axis A. In this way, by unscrewing/screwing the cap 31 the bushing 30 can be slid extractingly/insertingly internally of the cylindrical seating 16.
  • the internal surface of the cylindrical shank 311 of the cap 31 exhibits a coaxial annular gully 312, which defines a circumferential tooth 313 projecting radially internally with respect to the longitudinal axis A of the bushing 30.
  • the bushing 30 comprises a first and a second cylindrical portion 32 and 33, coaxially coupled to one another.
  • the first cylindrical portion 32 exhibits an end edge 321 from which a plurality of axially-developing tabs 322 project.
  • the tabs 322 are arranged circumferentially about the longitudinal axis A and are angularly distanced from one another in such a way as to place the internal volume of the bushing 30 in communication with the remaining part of the pump chamber 11 when the bushing 30 is inserted in the cylindrical seating 16.
  • Each tab 322 comprises a tooth 323 projecting radially externally with respect to the longitudinal axis A of the bushing 30.
  • the first cylindrical portion 32 can be snap-fitted to the cap 31, by partially inserting the tabs 322 internally of the cylindrical shank 311 and enabling the teeth 323 to snap-fit in the annular gully 312.
  • a perimeter gully is fashioned coaxially in the external surface of the cylindrical portion, for housing a high-pressure seal 34, which will be coaxially interposed between the bushing 30 and the relative cylindrical seating 16 of the head (see figure 1 ), such as to prevent leakage of fluid from the pump chamber 11 towards the casing 21.
  • the first cylindrical portion 32 of the bushing 30 also bears a further high-pressure annular seal 35, which will be coaxially interposed between the bushing 30 and the piston 15 (see figure 1 ).
  • This further high-pressure seal 35 is placed in contact with an abutment 324 of the cylindrical portion 32, which defines an annular surface perpendicular to the longitudinal axis A. In this way, the abutment 324 prevents the axial sliding of the high-pressure seal 35 in the direction of the cap 31.
  • the high-pressure seal 35 is axially blocked by the second cylindrical portion 33 of the bushing 30.
  • the second cylindrical portion 33 is suitable for partial insertion coaxially internally of the first cylindrical portion 32.
  • the end edge 331 of the second cylindrical portion 33 enters into contact with the high-pressure seal 35 (with a possible interposing of a spacer ring), compressing it and preventing it from sliding in an axial direction towards the casing 21.
  • the blocking of the first and second cylindrical portion 32 and 33 is obtained by snap-fitting means, which comprise a circumferential tooth 325, coaxially afforded in the first cylindrical portion 32, and a further circumferential tooth 335, coaxially afforded in the second cylindrical portion 33.
  • the circumferential tooth 325 projects radially towards the inside of the bushing 30 with respect to the longitudinal axis A, and is localised at an end edge 327 of the first cylindrical portion 32, opposite the end edge 321 from which the tabs 322 project.
  • the second circumferential tooth 335 projects radially towards the outside of the bushing 30 with respect to the longitudinal axis A, and is localised in an intermediate position of the second cylindrical portion 33, such as to enable the end edge 331 to come into contact with the high-pressure seal 35.
  • the second cylindrical portion 33 in turn bears a low-pressure annular seal which will be coaxially interposed between the bushing 30 and the relative cylindrical seating 16 of the head 10 (see figure 1 ).
  • This low-pressure seal 36 is axially blocked between the end edge 327 of the first cylindrical portion 32 and an abutment 332 of the second cylindrical portion 33, which extends radially externally with respect to the longitudinal axis A and is localised at the opposite end with respect to the end edge 331.
  • a perimeter gully for housing a further low-pressure annular seal 37 able to be coaxially interposed between the bushing 30 and the piston 14.
  • collection spaces for the fluid which might leak from the pump chamber 11 are defined between the high-pressure seals 34, 35 and the low-pressure seals 36, 37, (this fluid may seep from the high-pressure seals 34 and 35).
  • These collection spaces communicate with the aspirating conduit 12 via scavenger channels 15 afforded in the head 10 and are in communication with one another through passages fashioned in the lateral wall of the bushing 30, between the high-pressure seals and low-pressure seals.
  • these passages are defined by a plurality of lateral openings 326 (see figure 2 ) realised in the first cylindrical portion 32, and the circumferential tooth 325, and by through-holes 336 afforded in the second cylindrical portion 33, between the end edge 331 and the second tooth 335.
  • the through-holes 336 are positioned at the lateral openings 326 when the first and the second cylindrical portions 32 and 33 are reciprocally coupled.
  • the hydraulic piston pump 1 operates as follows.
  • a motor (not illustrated) activates the thrust mechanism 20 and at the same time the piston 14, which slides internally of the bushing 30.
  • the piston 14 slides in the direction of the casing 21 it generates a depression in the pump chamber 11 which causes the opening of the aspirating valve 121 and, consequently, the passage of the fluid from the aspirating conduit 12 to the pump chamber 11.
  • the cap 31 is unscrewed from the head 10, causing a simultaneous extraction of the bushing 30.
  • This operation is very simple as the multiplication ratio defined by the thread of the cap 31 enables the bushing 30 coupled thereto to be extracted progressively, also reducing the effort the operator has to apply to overcome any adhesion forces of the worn seals on the piston 14 and on the cylindrical seating 16 of the head 10.
  • the bushing 30 is extracted one or more of the high- or low-pressure seals 34, 35, 36, 37 can be replaced. This replacement can be done by the removal of the seals from the bushing or by completely substituting the bushing 30 together with the seals.
  • the bushing 30 i.e. one or both the cylindrical portions 32,33
  • the bushing 30 is preferably made of a plastic material, for example by moulding, such as to realise a low-cost component of the single-use disposable type.
  • bushing 30 is realised in two cylindrical portions 32 and 33 it is also possible to replace only of the portions, or briefly separate the first cylindrical portion 32 from the second cylindrical portion 33 such as to facilitate the removal of the seals.
  • bushing 30 might also be realised in a single piece, instead of with the two cylindrical portions 32 and 33 described above.
  • the invention as it is conceived herein is susceptible to numerous modifications and variants, all falling within the scope of the inventive concept. Furthermore, all the details can be replaced by other technically-equivalent elements. In practice the materials used, as well as the contingent shapes and dimensions, can be of any type according to requirements, without forsaking the scope of protection of the following claims.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Details Of Reciprocating Pumps (AREA)
  • Reciprocating Pumps (AREA)
  • Lubrication Of Internal Combustion Engines (AREA)
  • Valve Device For Special Equipments (AREA)
EP13175582.9A 2012-11-02 2013-07-08 Hydraulische Kolbenpumpe Active EP2728190B8 (de)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
IT000078A ITRE20120078A1 (it) 2012-11-02 2012-11-02 Pompa idraulica a pistoni

Publications (3)

Publication Number Publication Date
EP2728190A1 true EP2728190A1 (de) 2014-05-07
EP2728190B1 EP2728190B1 (de) 2016-01-13
EP2728190B8 EP2728190B8 (de) 2016-03-16

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ID=47471938

Family Applications (1)

Application Number Title Priority Date Filing Date
EP13175582.9A Active EP2728190B8 (de) 2012-11-02 2013-07-08 Hydraulische Kolbenpumpe

Country Status (2)

Country Link
EP (1) EP2728190B8 (de)
IT (1) ITRE20120078A1 (de)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN104895759A (zh) * 2015-05-25 2015-09-09 南通广兴气动设备有限公司 用于高压气泵的二级加压装置
CN104895760A (zh) * 2015-05-25 2015-09-09 南通广兴气动设备有限公司 二级加压装置
IT201800006145A1 (it) * 2018-06-08 2019-12-08 Pompa volumetrica a pistoni

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6000764A (en) * 1996-12-30 1999-12-14 Kelsey Hayes Company Hydraulic pump assembly and method of making same
US6382940B1 (en) * 2000-07-18 2002-05-07 George H. Blume High pressure plunger pump housing and packing
EP2466138A1 (de) * 2010-12-16 2012-06-20 Interpump Engineering S.r.l. Pumpe mit Kolbenführung

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6000764A (en) * 1996-12-30 1999-12-14 Kelsey Hayes Company Hydraulic pump assembly and method of making same
US6382940B1 (en) * 2000-07-18 2002-05-07 George H. Blume High pressure plunger pump housing and packing
EP2466138A1 (de) * 2010-12-16 2012-06-20 Interpump Engineering S.r.l. Pumpe mit Kolbenführung

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN104895759A (zh) * 2015-05-25 2015-09-09 南通广兴气动设备有限公司 用于高压气泵的二级加压装置
CN104895760A (zh) * 2015-05-25 2015-09-09 南通广兴气动设备有限公司 二级加压装置
IT201800006145A1 (it) * 2018-06-08 2019-12-08 Pompa volumetrica a pistoni
EP3578811A1 (de) 2018-06-08 2019-12-11 Annovi Reverberi S.p.A. Volumetrische kolbenpumpe

Also Published As

Publication number Publication date
EP2728190B1 (de) 2016-01-13
ITRE20120078A1 (it) 2014-05-03
EP2728190B8 (de) 2016-03-16

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