EP0337439A2 - Pompe à pistons radiaux à cylindres immobiles avec dispositif pour commande de refoulement - Google Patents

Pompe à pistons radiaux à cylindres immobiles avec dispositif pour commande de refoulement Download PDF

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Publication number
EP0337439A2
EP0337439A2 EP89106542A EP89106542A EP0337439A2 EP 0337439 A2 EP0337439 A2 EP 0337439A2 EP 89106542 A EP89106542 A EP 89106542A EP 89106542 A EP89106542 A EP 89106542A EP 0337439 A2 EP0337439 A2 EP 0337439A2
Authority
EP
European Patent Office
Prior art keywords
pump
fixed cylinder
volume control
radial piston
cylinder type
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.)
Withdrawn
Application number
EP89106542A
Other languages
German (de)
English (en)
Other versions
EP0337439A3 (fr
Inventor
Sigeaki Yamamuro
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.)
Nissan Motor Co Ltd
Original Assignee
Nissan Motor Co 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 Nissan Motor Co Ltd filed Critical Nissan Motor Co Ltd
Publication of EP0337439A2 publication Critical patent/EP0337439A2/fr
Publication of EP0337439A3 publication Critical patent/EP0337439A3/fr
Withdrawn legal-status Critical Current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
    • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • F04B49/22—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00 by means of valves
    • F04B49/225—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00 by means of valves with throttling valves or valves varying the pump inlet opening or the outlet opening

Definitions

  • the present invention relates to a volume control apparatus of fixed cylinder type radial piston pump.
  • the rotating cylinder type radial piston pump is constructed such that radially reciprocable pistons are disposed in a cylinder rotated by a pump driving force and are reciprocated as being guided along an inside circumference of an eccentric cam ring to obtain a pump action, so that it is difficult to get a variable volume construction by regulating an eccentric amount of the cam ring.
  • an eccentricity adjusting mechanism has to be further provided to the cam ring witha large diameter, causing a pump dimension and weight increase and a bad responsibility of volume control.
  • the fixed cylinder type radial piston pump is constructed such that radially reciprocable pistons are disposed in a fixed cylinder and are reciprocated by an eccentric cam rotated by a pump driving force to obtain a pump action, so that the above-mentioned problem does not arise but pump construction becomes complex to get an eccentric amount of the eccentric cam variable.
  • an object of the present invention is to provide a fixed cylinder type radial piston pump in which volume control is possible without regulating the eccentric amount of the eccentric cam.
  • a specific object of the present invention is to provide a volume control apparatus of fixed cylinder type radial piston pump.
  • a fixed cylinder type radial piston pump with volume control apparatus comprising: a pump portion including suction and delivery systems, said pump portion carrying out a pump action by pump driving force of a pump drive shaft; a fixed cylinder provided in said pump portion, in which a plurality of pistons are slidably disposed, said plurality of pistons being radially reciprocable in said fixed cylinder to suck a fluid from a suction passage and discharge said fluid to a delivery passage; an eccentric cam installed on said pump drive shaft and rotated by a pump driving force of said pump drive shaft, said eccentric cam guiding said plurality of pistons slidably disposed in said fixed cylinder; and an aperture means for carrying out opening control of said suction passage.
  • a fixed cylinder type radial piston pump 1 includes a pump body 2 in which a pump drive shaft 10 is rotatably supported by bearings 4, 6 and 8.
  • An eccentric portion 10a is installed on the pump drive shaft 10 thereby to pivotally support an eccentric cam 12.
  • a plurality of pistons 14 are disposed each being radially slidable in the pump body 2.
  • Each of the pistons 14 touches an outside circumference of the eccentric cam 12 by force of a spring 16 and incorporates a suction valve 18.
  • a delivery valve 20 is provided in the pump body 2.
  • the radial piston pump 1 thus constructed operates as follows: When the drive shaft 10 is rotated by pump driving force, the eccentric cam 12 radially reciprocates each of the pistons 14. While each of the pistons 14 strokes radially inwardly, the suction valve 18 is opened thereby to suck a fluid from a suction passage 22 and a suction port 24 into a pump chamber 26. While each of the pistons 14 strokes radially outwardly, the suction valve 18 is closed to generate a pressure in the pump chamber 26, thereby to open the delivery valve 20 and discharge the fluid from the chamber 26 to a delivery port 28 and a delivery passage 30 therethrough. A check valve 32, an accumulator 34 and a relief valve 36 are provided in the delivery passage 30.
  • the fluid flowing in the passage 30 comes to the accumulator 34 through the check valve 32, wherein fluid pressure is increased to form a line pressure P L for controlling a hydraulic apparatus (not shown). If the line pressure P L is too high, the relief valve 36 is opened to prevent a pump circuit from being damaged.
  • a variable aperture 38 is inserted in the suction passage 22 thereby to permit volume control of the pump 1.
  • the variable aperture 38 is of the rotary type capable of controlling an opening of the suction passage 22 and its rotational position is regulated by a step motor 40.
  • the step motor 40 opens completely the variable aperture 38 at a drive step number 0 and minimally opens it at a drive step number Max.
  • the motor 40 is controlled through an amplifier 44 by a microcomputer 42 to which is input a signal L from a limit switch 46 which is turned on at the minimum opening of the variable aperture 38. Additionally, after converting to a digital signal by an analog-to-digital converter 48, a signal from a pressure sensor 47 for detecting the line pressure P L is input to the computer 42.
  • the pressure sensor 47 provides a voltage V to the line pressure P L as shown in Fig. 3, in which P1 and P2 denote lower and upper limits of working line pressure and V1 and V2 output voltages of the sensor 47 with respect to the lower and upper limits.
  • an opening pressure P3 of the relief valve 36 is also indicated for reference.
  • the microcomputer 42 performs a control program on input informations as mentioned above, thereby to carry out opening control of the suction passage 22, i.e. volume control of the pump 1 by means of the step motor 40.
  • the drive step number STEP of the motor 40 is initialized and the variable aperture 38 completely opens the suction passage 22 to set the pump 1 in the maximum discharge (maximum capacity).
  • the maximum amount of fluid is discharged in the passage 30, allowing rapid increase of the line pressure P L .
  • an output voltage V of the pressure sensor 47 is read to detect a current value of the line pressure P L .
  • an aimed drive step number STEP (A) of the step motor 40 is looked up from a table data corresponding to Fig. 3 obtained from the current value of the line pressure P L .
  • the table data of the aimed drive step number STEP (A) is such that: If the line pressure P L is less than the lower limit P1, the variable aperture 38 is completely opened to maximize the pump discharge; if the line pressure P L is more than the upper limit P2, the aperture 38 is minimally opened to minimize the pump discharge; and if the line pressure P L falls in a practical range from P1 to P2, the aperture 38 is set to a predetermined opening to appropriately control the pump discharge, thereby for keeping the line pressure P L in the practical range.
  • step 53 if it is judged that the limit switch 46 is turned on, the program proceeds to step 54 at which the step number STEP is set to the maximum STEP (Max) thereby to avoid integrating an error of the step number STEP.
  • step 55 the current step number STEP is compared with the aimed step number STEP (A). If both are of the same value, the program proceeds to step 56 at which a signal for driving the step motor 40 is provided to keep the variable aperture 38 at a current opening. If the current step number STEP is less than the aimed step number STEP (A) or STEP is more than STEP (A), the program proceeds to step 57 or 58 at which the step number STEP is increased or decreased by one to set it to the aimed step number STEP (A). And at step 56, a signal for driving the step motor 40 is provided as described above.
  • the step motor 40 may carry out opening control of the variable aperture 38 to keep the line pressure P L in the practical range from P1 to P2 and allows an approproiate selection of a pump capacity resulting in an energy-saving.
  • the pump discharge is indicated by a fully-drawn line in Fig. 4.
  • the discharge is reduced as indicated by an one-dot-­chain line in Fig. 4 because of decreased opening period of time of the suction valve 18.
  • FIG. 5 there is shown another embodiment of the present invention, in which another eccentric portion 10b is installed on the pump drive shaft 10 to rotatably support an eccentric cam 12′ and a pump portion comprising a piston 14′, a spring 16′, a suction valve 18′ and a delivery valve 20′ is added to include two pump portions displaced by a half phase each other.
  • the two pump portions have a delivery port 28 and a delivery passage 30 in common and two suction systems separated by an intermediate wall 60.
  • One suction system includes, as described above, the suction passage 22 with the variable aperture 38 and the suction port 24 and another a suction passage 22′ and a suction port 24′.
  • a gate valve 62 is provided in the suction passage 22′.
  • the discharge of a pump portion related to the valve 62 is increased, e.g. the maximum pump discharge can be increased from a characteristic value indicated by a fully-drawn line in Fig. 6 equivalent to that in Fig. 4 to a characteristic value indicated by a one-dot-chain line in Fig. 6. Additionally, it can be continuously decreased up to a characteristic value indicated by a three-dot-chain line by carrying out opening control of the variable aperture 38 with the gate valve 62 opened.
  • pump discharge characteristic similar to Fig. 4 can be obtained by carrying out opening control of the variable aperture 38 with the gate valve 62 closed.
  • the pump discharge also can be reduced from a characteristic value indicated by the fully-­drawn line to that indicated by a two-dot-chain line in Fig. 6 by performing opening control of the variable aperture 38 with the gate valve 62 closed.
  • the pump discharge is capable of being continuously controlled from the characteristic value indicated by the one-dot-chain line to that indicated by the two-dot-chain line so that control range is greatly enlarged.
  • suction system related to a suction port 24′ is associated with a pump chamber 26′ through a suction check valve 64 as shown in Fig. 7, suction systems of two pump portions can be separated without the intermediate wall 60 as shown in Fig. 5, resulting in reduction of the total length of the pump.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Reciprocating Pumps (AREA)
  • Control Of Positive-Displacement Pumps (AREA)
  • Details Of Reciprocating Pumps (AREA)
EP19890106542 1988-04-13 1989-04-12 Pompe à pistons radiaux à cylindres immobiles avec dispositif pour commande de refoulement Withdrawn EP0337439A3 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP88909/88 1988-04-13
JP8890988A JPH01262374A (ja) 1988-04-13 1988-04-13 固定シリンダ型ラジアルピストンポンプの容量制御装置

Publications (2)

Publication Number Publication Date
EP0337439A2 true EP0337439A2 (fr) 1989-10-18
EP0337439A3 EP0337439A3 (fr) 1990-09-26

Family

ID=13956069

Family Applications (1)

Application Number Title Priority Date Filing Date
EP19890106542 Withdrawn EP0337439A3 (fr) 1988-04-13 1989-04-12 Pompe à pistons radiaux à cylindres immobiles avec dispositif pour commande de refoulement

Country Status (2)

Country Link
EP (1) EP0337439A3 (fr)
JP (1) JPH01262374A (fr)

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4138313A1 (de) * 1990-11-22 1992-05-27 Nissan Motor Verdraengungspumpenanordnung
WO1995029324A1 (fr) * 1994-04-26 1995-11-02 Mannesmann Rexroth Gmbh Systeme de frein moteur pour moteur a combustion interne multicylindre
EP1013921A2 (fr) * 1998-12-25 2000-06-28 Denso Corporation Pompe d'injection de carburant
WO2001046590A1 (fr) * 1999-12-22 2001-06-28 Continental Teves Ag & Co. Ohg Pompe dotee d'une soupape a regulation
DE19510206B4 (de) * 1995-03-21 2005-08-18 Zf Friedrichshafen Ag Regeleinrichtung für einen Hydraulikkreis
EP1818539A2 (fr) 2002-05-14 2007-08-15 Robert Bosch Gmbh Pompe a pistons radiaux destinée a un système d'injection de carburant présentant une meilleure résistance aux pressions élevées

Families Citing this family (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2672127B2 (ja) * 1988-09-20 1997-11-05 カヤバ工業株式会社 ラジアルピストンポンプ
JPH02122180U (fr) * 1989-03-17 1990-10-05
JP2689664B2 (ja) * 1989-12-28 1997-12-10 日産自動車株式会社 可変容量容積ポンプの流量制御装置
JP2684804B2 (ja) * 1990-01-19 1997-12-03 日産自動車株式会社 容積ポンプの制御装置
JP2768033B2 (ja) * 1991-03-26 1998-06-25 日産自動車株式会社 容積ポンプの制御装置
JPH04187871A (ja) * 1990-11-22 1992-07-06 Nissan Motor Co Ltd 固定シリンダ型ラジアルピストンポンプの容量制御装置
US5687808A (en) * 1994-03-18 1997-11-18 Nissan Motor Co., Ltd. Four wheel drive mechanism

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1653379A1 (de) * 1967-05-13 1971-07-01 Bosch Gmbh Robert Hydraulische Kolbenpumpe mit einem in der Saugleitung angeordneten Drosselglied
DE2946746A1 (de) * 1979-11-20 1981-05-27 Fichtel & Sachs Ag, 8720 Schweinfurt Radialkolbenpumpe mit druckabhaengiger ansaugdrosselung
DE2951012A1 (de) * 1979-12-19 1981-07-23 Zahnradfabrik Friedrichshafen Ag, 7990 Friedrichshafen Pumpenanordnung

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS51118103A (en) * 1975-04-10 1976-10-16 Daiken Kogyo Kk Super liquid pressure pump

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1653379A1 (de) * 1967-05-13 1971-07-01 Bosch Gmbh Robert Hydraulische Kolbenpumpe mit einem in der Saugleitung angeordneten Drosselglied
DE2946746A1 (de) * 1979-11-20 1981-05-27 Fichtel & Sachs Ag, 8720 Schweinfurt Radialkolbenpumpe mit druckabhaengiger ansaugdrosselung
DE2951012A1 (de) * 1979-12-19 1981-07-23 Zahnradfabrik Friedrichshafen Ag, 7990 Friedrichshafen Pumpenanordnung

Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4138313A1 (de) * 1990-11-22 1992-05-27 Nissan Motor Verdraengungspumpenanordnung
WO1995029324A1 (fr) * 1994-04-26 1995-11-02 Mannesmann Rexroth Gmbh Systeme de frein moteur pour moteur a combustion interne multicylindre
US5697336A (en) * 1994-04-26 1997-12-16 Mannesmann Rexroth Gmbh Engine brake for a multi-cylinder internal combustion engine
DE19510206B4 (de) * 1995-03-21 2005-08-18 Zf Friedrichshafen Ag Regeleinrichtung für einen Hydraulikkreis
EP1013921A2 (fr) * 1998-12-25 2000-06-28 Denso Corporation Pompe d'injection de carburant
EP1013921A3 (fr) * 1998-12-25 2003-05-02 Denso Corporation Pompe d'injection de carburant
WO2001046590A1 (fr) * 1999-12-22 2001-06-28 Continental Teves Ag & Co. Ohg Pompe dotee d'une soupape a regulation
EP1818539A2 (fr) 2002-05-14 2007-08-15 Robert Bosch Gmbh Pompe a pistons radiaux destinée a un système d'injection de carburant présentant une meilleure résistance aux pressions élevées
EP1818539A3 (fr) * 2002-05-14 2008-03-19 Robert Bosch Gmbh Pompe a pistons radiaux destinée a un système d'injection de carburant présentant une meilleure résistance aux pressions élevées

Also Published As

Publication number Publication date
EP0337439A3 (fr) 1990-09-26
JPH01262374A (ja) 1989-10-19

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