Classifications

• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
  • F01P—COOLING OF MACHINES OR ENGINES IN GENERAL; COOLING OF INTERNAL-COMBUSTION ENGINES
  • F01P7/00—Controlling of coolant flow
  • F01P7/14—Controlling of coolant flow the coolant being liquid
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
  • F01P—COOLING OF MACHINES OR ENGINES IN GENERAL; COOLING OF INTERNAL-COMBUSTION ENGINES
  • F01P11/00—Component parts, details, or accessories not provided for in, or of interest apart from, groups F01P1/00 - F01P9/00
  • F01P11/12—Filtering, cooling, or silencing cooling-air
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
  • F01P—COOLING OF MACHINES OR ENGINES IN GENERAL; COOLING OF INTERNAL-COMBUSTION ENGINES
  • F01P3/00—Liquid cooling
  • F01P3/20—Cooling circuits not specific to a single part of engine or machine
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
  • F01P—COOLING OF MACHINES OR ENGINES IN GENERAL; COOLING OF INTERNAL-COMBUSTION ENGINES
  • F01P5/00—Pumping cooling-air or liquid coolants
  • F01P5/10—Pumping liquid coolant; Arrangements of coolant pumps
  • F01P5/12—Pump-driving arrangements
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
  • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
  • F04D1/00—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
  • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
  • F04D13/00—Pumping installations or systems
  • F04D13/02—Units comprising pumps and their driving means
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
  • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
  • F04D15/00—Control, e.g. regulation, of pumps, pumping installations or systems
  • F04D15/0005—Control, e.g. regulation, of pumps, pumping installations or systems by using valves
  • F04D15/0022—Control, e.g. regulation, of pumps, pumping installations or systems by using valves throttling valves or valves varying the pump inlet opening or the outlet opening
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
  • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
  • F04D15/00—Control, e.g. regulation, of pumps, pumping installations or systems
  • F04D15/0027—Varying behaviour or the very pump
  • F04D15/0038—Varying behaviour or the very pump by varying the effective cross-sectional area of flow through the rotor
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
  • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
  • F04D15/00—Control, e.g. regulation, of pumps, pumping installations or systems
  • F04D15/0077—Safety measures
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
  • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
  • F04D29/00—Details, component parts, or accessories
  • F04D29/18—Rotors
  • F04D29/22—Rotors specially for centrifugal pumps
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
  • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
  • F04D29/00—Details, component parts, or accessories
  • F04D29/40—Casings; Connections of working fluid
  • F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
  • F04D29/426—Casings; Connections of working fluid for radial or helico-centrifugal pumps especially adapted for liquid pumps
  • F04D29/4293—Details of fluid inlet or outlet
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
  • F01P—COOLING OF MACHINES OR ENGINES IN GENERAL; COOLING OF INTERNAL-COMBUSTION ENGINES
  • F01P7/00—Controlling of coolant flow
  • F01P7/14—Controlling of coolant flow the coolant being liquid
  • F01P2007/146—Controlling of coolant flow the coolant being liquid using valves
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
  • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
  • F05D2270/00—Control
  • F05D2270/60—Control system actuates means
  • F05D2270/64—Hydraulic actuators

Definitions

• the invention relates to a controllable coolant pump, in particular for use in internal combustion engines.
• the cooling capacity of the coolant pumps must imperatively be adapted to these increasing engine outputs, so that the associated coolant pump must apply a correspondingly high flow rate already in the lower engine speed range for the engines with increasing engine power, and must therefore be dimensioned large, which inevitably increases the space requirement in the engine Engine compartment required.
• a wide variety of pressure control functions are used. But their use again requires a further space in the engine compartment and also often for the operation of auxiliary power, via supply lines, which also require even more space, must be provided.
• DE 881 306 B Another possibility for realizing a pressure regulating function has been described in DE 881 306 B.
• This is a centrifugal pump with hydraulically operated control slide.
• the actuating pressure used is the delivery pressure of the pump.
• a spring causes the slider to be closed in the normal position / initial position.
• the displacement piston is acted upon in this solution on both sides with the delivery pressure. If necessary, the spring chamber can be relieved of pressure via an external valve, thereby introducing an adjustment of the control slide in the "open" direction.
• EP Applicants have proposed in EP 1657446 A2 a coolant pump with pressure regulating function which has been proven in practice in the meantime by means of a valve slide, in which this valve slide is adjusted by a central working piston arranged around the pump shaft one abuts around the pump shaft around, the valve spool in the "fully open” starting position adjusting / restoring return spring is applied.
• the impeller is also axially displaceable in this design but rotatably mounted on the shaft. Between the pressure incline in the housing and the open impeller, the delivery pressure acts and shifts the impeller when it reaches a preset value against the spring force of a present at the back of the impeller disc spring. Due to the increasing in this axial displacement of the impeller sealing gap with respect to the pressure ramp, the delivery pressure of the pump decreases. The prerequisite for this is that there is a space (i.e., the spring chamber) on the rear side of the impeller with a lower pressure level than the delivery pressure.
• control slide is arranged on a spring-loaded, axially displaceable annular piston, wherein the control pressure for actuating the control slide generated by a, especially for this purpose designed as a swash plate, rear wall of the pump impingement Axialkolbenpumpe, and is regulated by means disposed in the pump housing solenoid valve.
• the invention is therefore based on the object over a drive wheel, driven, continuously variable coolant pump (with control slide) to develop, which avoids all the aforementioned disadvantages of the prior art, also over constant pumps with pressure relief valve has significant energy advantages, in particular no external energy (such as hydraulics, vacuum, electrical energy) for pressure or volume flow control required, a high reliability (fail-safe) ensures, and the one optimal warming of engines with, based on the displacement, high engine performance, which require very large sized coolant pumps to ensure, and even after the heating of the engine, the engine temperature in continuous operation continuously, highly dynamically, and very reliable over very long periods very accurately is to influence, and at the same time a minimum, optimally use the available space in the engine compartment size should, the to be developed coolant pump also manufacturing and assembly technology is simple, and inexpensive to produce, and over the entire life always high reliability and a to ensure high reliability.
• this object is achieved by a driven by a drive wheel controllable coolant pump for internal combustion engines according to the features of the independent claim of the invention.
• Figure 1 arranged on a motor housing 37, inventive controllable coolant pump in the side view in section;
• Figure 2 the pump shaft 4 with the pilot valve 20 in a spatial
• Figure 3 the detail Z of Figure 1 with a schematic representation of the "control currents" during the "opening phase” of the control slide 12;
• Figure 4 the detail Z of Figure 1 with a schematic representation of
• FIG. 1 shows the arranged on a motor housing 37 according to the invention, controllable coolant pump with a pump housing 1, a mounted on the pump housing 1 in a pump bearing 2, by a drive wheel 3, here in the form of a pulley 40 driven pump shaft 4, with one on a free , flow-side end of this pump shaft 4 rotatably mounted impeller 5, and with a pump housing 1 axially guided, spring-loaded by a return spring 6 annular piston 7, on which the rear wall 8 of a arranged in the pump interior 9 control slide 12, with a Ausström Scheme 10 of the impeller 5 variable overlapping outer cylinder 1 1, is fixed rigidly, wherein between the pump shaft 4 and the pump housing 1 in a seal receptacle 13, a shaft seal 14 is arranged, and also in the pump interior 9 formed by the pump housing 1, or arranged on the pump housing 1 pump dome 15 are arranged, where one between de m impeller 5 and the rear wall 8 of the control slide 12 in the pump interior 9 positionally fixed wall plate 16 is arranged.
• a slide guide 17 is arranged on the pump housing 1 for the spring piston 6 spring loaded by the return piston 6, which guides the annular piston 7 on the outer jacket and is also freely spaced apart with its inner shell of the pump shaft 4.
• the slide guide 17 rests with the free, flow-side end of the wall plate 16, so that the adjacent components, ie the slide guide 17, the wall plate 16, a at the inner circumference, spaced from the pump shaft 4 by a throttle gap, on the wall plate 16 radially movably arranged sealing disc 33, the pump shaft 4 and the shaft seal 14, together include a ring-cylindrical pressure chamber 18 / form.
• the radially movable in the wall disk 16 arranged sealing disk 33 whose inner diameter has little play (tight running fit) relative to the outer diameter of the pump shaft 4, represents a throttle gap, which allows only small leaks in the pressure chamber 18.
• a pilot valve 20 consisting of a set screw 22, a valve spring 23 and a valve piston 24, is provided on the free end of the pump shaft 4 in a valve seat bore such that the valve piston 24 is in the Closing state of the pilot valve 20 a centrally disposed in the pump shaft 4, opening into the valve seat bore shaft bore 25 closes, which opens via one / more arranged in the pump shaft 4 transverse bore / en 26 into the pressure chamber 18.
• the pilot valve 20 the pump shaft 4 is shown with the pilot valve 20 in Figure 2 in a three-dimensional exploded view.
• the laser bores 28 prevent the entry of dirt load and thus increase the reliability of the control device according to the invention. At the same time serve the laser bores 28 in the inventive arrangement as a feed orifice and ensure that no more liquid flows as can proceed via the pilot valve 20.
• annular piston 7 a filter piston slide 30 is rigidly arranged, which slides on displacement of the annular piston 7 on the outer circumference of the filter sleeve 29 along, so the filter sleeve 29 freed of dirt load, i. the arranged in the filter sleeve 29 laser bores 28 / (filter bores) cleans of the debris accumulations in the inflow, and thus ensures high reliability, even under extreme conditions of use.
• the annular piston 7 together with the filter piston slide 30, the filter sleeve 29, the wall plate 16 and the slide guide 17 enclose a ring-cylindrical spring pressure chamber 31.
• FIG. 3 shows the detail Z from FIG. 1 with a schematic representation of the "control currents" during the "opening phase” of the control slide 12.
• the control slide 12 moves in the direction of the pulley 40, thereby opening with its outer cylinder 1 1 the outflow region 10 of the impeller. 5
• the valve piston 24 of the pilot valve 20 is the same pressure as immediately behind the filter sleeve 29 in the spring pressure chamber 31, this pressure be referred to in the further explanations as a control pressure.
• This regulating pressure acts on the annular surface of the annular piston 7 acted upon by this pressure.
• the resulting pressure force is called the control pressure force below.
• This control pressure force rectified, also attacks the annular piston 7, the spring force of the return spring 6 at. In sum, the control pressure force and the spring force form an opening force acting on the annular piston 7. This opening force tends to move the rigidly connected to the annular piston 7 control slide 12 in the drive-side end position.
• the opening force is directed against the control slide 12 to a closing pressure force, which emerges from the acted upon at the annular piston 7 with working pressure surface.
• a closing pressure force which emerges from the acted upon at the annular piston 7 with working pressure surface.
• FIG. 4 shows the detail Z from FIG. 1 with a schematic illustration of the control currents during the "closing phase" of the control slide 12.
• this movement direction of the control slide 12 (shown in FIG. 4 with a directional arrow R on the control slide 12) moves the control slide 12 in the direction of the impeller 5 and thereby closes with its outer cylinder 1 1 the outflow region 10 of the impeller. 5
• the filter sleeve 29, preset control pressure continuously increases, and this, as already explained, directly applied to the valve piston 24 of the pilot valve 20, when reaching a maximum allowable Working pressure, the pilot valve 20 are preset so that this then opens, while the cooling medium located in the pressure chamber 18, as shown in Figure 4, is emptied into the suction channel 38.

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• Engineering & Computer Science (AREA)
• Mechanical Engineering (AREA)
• General Engineering & Computer Science (AREA)
• Chemical & Material Sciences (AREA)
• Combustion & Propulsion (AREA)
• Structures Of Non-Positive Displacement Pumps (AREA)
• Control Of Non-Positive-Displacement Pumps (AREA)

Priority Applications (5)

Applications Claiming Priority (2)

Publications (1)

Family

ID=50821691

Family Applications (1)

Country Status (7)

Families Citing this family (17)

Citations (6)

Family Cites Families (2)

• 2013
  • 2013-10-30 DE DE201310018205 patent/DE102013018205B3/de not_active Expired - Fee Related
• 2014
  • 2014-10-22 WO PCT/DE2014/000538 patent/WO2015062565A1/de active Application Filing
  • 2014-10-22 CN CN201480058116.9A patent/CN105874208A/zh active Pending
  • 2014-10-22 KR KR1020167011855A patent/KR20160078365A/ko not_active Application Discontinuation
  • 2014-10-22 US US14/915,331 patent/US20160215679A1/en not_active Abandoned
  • 2014-10-22 JP JP2016526137A patent/JP2016535833A/ja active Pending
  • 2014-10-22 EP EP14809754.6A patent/EP3063412A1/de not_active Withdrawn

Patent Citations (7)

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