EP3572664B1 - High-pressure pump - Google Patents
High-pressure pump Download PDFInfo
- Publication number
- EP3572664B1 EP3572664B1 EP18741821.5A EP18741821A EP3572664B1 EP 3572664 B1 EP3572664 B1 EP 3572664B1 EP 18741821 A EP18741821 A EP 18741821A EP 3572664 B1 EP3572664 B1 EP 3572664B1
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- EP
- European Patent Office
- Prior art keywords
- section
- plunger
- plunger sleeve
- pressure
- pressure chamber
- 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.)
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- 239000000446 fuel Substances 0.000 claims description 49
- 238000005086 pumping Methods 0.000 claims description 24
- 238000003754 machining Methods 0.000 claims description 15
- 230000007704 transition Effects 0.000 claims description 7
- 230000003247 decreasing effect Effects 0.000 claims description 4
- 238000010586 diagram Methods 0.000 description 6
- 239000000463 material Substances 0.000 description 4
- 230000009286 beneficial effect Effects 0.000 description 2
- 238000002347 injection Methods 0.000 description 2
- 239000007924 injection Substances 0.000 description 2
- 238000000034 method Methods 0.000 description 2
- 238000007789 sealing Methods 0.000 description 2
- 230000003044 adaptive effect Effects 0.000 description 1
- 238000002485 combustion reaction Methods 0.000 description 1
- 238000004891 communication Methods 0.000 description 1
- 238000009826 distribution Methods 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 238000004134 energy conservation Methods 0.000 description 1
- 230000006872 improvement Effects 0.000 description 1
- 238000009434 installation Methods 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
- 230000008569 process Effects 0.000 description 1
- 230000009467 reduction Effects 0.000 description 1
- 238000004381 surface treatment Methods 0.000 description 1
Images
Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
- F02M59/44—Details, components parts, or accessories not provided for in, or of interest apart from, the apparatus of groups F02M59/02 - F02M59/42; Pumps having transducers, e.g. to measure displacement of pump rack or piston
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
- F02M59/44—Details, components parts, or accessories not provided for in, or of interest apart from, the apparatus of groups F02M59/02 - F02M59/42; Pumps having transducers, e.g. to measure displacement of pump rack or piston
- F02M59/442—Details, components parts, or accessories not provided for in, or of interest apart from, the apparatus of groups F02M59/02 - F02M59/42; Pumps having transducers, e.g. to measure displacement of pump rack or piston means preventing fuel leakage around pump plunger, e.g. fluid barriers
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
- F02M59/02—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type
- F02M59/10—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type characterised by the piston-drive
- F02M59/102—Mechanical drive, e.g. tappets or cams
Definitions
- the present invention relates to the technical field of fuel injection pumps, and in particular, to a high-pressure pump.
- a high-pressure pump is a critical part of a direct fuel injection engine.
- the high-pressure pump includes an inlet valve 5', an outlet valve 6', a pressure chamber 1' disposed between the inlet valve 5' and the outlet valve 6', a plunger sleeve 3' disposed in the pressure chamber 1', a protruding member 8' disposed at one end of the plunger sleeve and at its outer side, and in interference fit to the pressure chamber 1', and a plunger 4' disposed inside the plunger sleeve 3'.
- Pressure is generated by the movement of the plunger 4' in the pressure chamber 1' to convert low-pressure fuel into high-pressure fuel (having a pressure up to 150 bar or higher).
- the above schemes 1 and 2 are accompanied by the increase in weight and cost, and the above scheme 3 is accompanied by the risks of accelerated wear to the plunger set and a significant decrease in the service life, and it is required to use the material having better performance in wear resistance or to perform a surface treatment process to acquire a better wear resistance.
- the cost will be increased.
- WO2008086011 discloses a clamping and seal loading technique for securing the plunger sleeve to the pump housing of a single plunger fuel pump. This is achieved by providing a load ring between a sleeve retainer and the sleeve, such that the axial force applied by the retainer during installation and attachment to the plunger bore wall of the housing, is distributed more evenly on the sleeve and the sealing surface of the sleeve against the housing adjacent to the pumping chamber. The even distribution of force minimizes misalignment of the sleeve and thus maintains concentricity between the sleeve and the plunger.
- An objective of the present invention is to provide a high-pressure pump to solve the problem in the prior art that in the fuel pumping stage of the high-pressure pump, the high-pressure fuel is likely to return to low-pressure areas through a plunger clearance, and the volumetric efficiency is reduced.
- the present invention provides a high-pressure pump, comprising: a pressure chamber, a plunger sleeve disposed in the pressure chamber, a protruding member disposed at an outer side of the plunger sleeve and in interference fit to a wall of the pressure chamber, a plunger disposed in the plunger sleeve, an inlet valve, and an outlet valve, wherein the plunger sleeve comprises a first section and a second section connected to the first section; the protruding member is disposed on an outer side of the second section close to the first section; the protruding member divides the pressure chamber into a first pressure chamber and a second pressure chamber, the first section is located in the first pressure chamber, and the inlet valve and the outlet valve are disposed at the first pressure chamber.
- the plunger moves from the second pressure chamber towards the first pressure chamber.
- the first pressure chamber in the fuel pumping stage of the high-pressure pump, has a pressure higher than a pressure of the second pressure chamber.
- the first section of the plunger sleeve deforms to contract inwards, and a clearance between the first section of the plunger sleeve and the plunger is smaller than a machining clearance of a plunger set.
- the pressure in the first pressure chamber is progressively decreased along a direction towards the second pressure chamber.
- the plunger moves from the first pressure chamber towards the second pressure chamber.
- the first pressure chamber in the fuel sucking stage of the high-pressure pump, has a pressure equal to a pressure of the second pressure chamber.
- a clearance between the first section of the plunger sleeve and the plunger is equal to a clearance between the second section of the plunger sleeve and the plunger, and the clearance between the second section of the plunger sleeve and the plunger is a machining clearance of a plunger set.
- the first section of the plunger sleeve has an inner diameter same as an inner diameter of the second section of the plunger sleeve, and the first section of the plunger sleeve has an outer diameter same as an outer diameter of the second section of the plunger sleeve.
- the first section of the plunger sleeve has an inner diameter same as an inner diameter of the second section of the plunger sleeve, and the first section of the plunger sleeve has an outer diameter different from an outer diameter of the second section of the plunger sleeve.
- the first section of the plunger sleeve has a length satisfying a relationship with a total length of the plunger sleeve as follows: 3 ⁇ L 2 L 1 ⁇ 8 wherein L2 represents the total length of the plunger sleeve, and L1 represents the length of the first section of the plunger sleeve.
- the inner diameter of the first section of the plunger sleeve, the outer diameter of the first section of the plunger sleeve, and the outer diameter of the second section of the plunger sleeve satisfy the following relationship: D 2 ⁇ D 1 D 3 ⁇ D 1 > 1.2 , wherein D1 represents the inner diameter of the first section of the plunger sleeve, D2 represents the outer diameter of the second section of the plunger sleeve, and D3 represents the outer diameter of the first section of the plunger sleeve.
- the first section is connected to the second section through a transition section, and a cross section of the transition section is shaped with any one of a round corner, a right angle, a chamfer, a multi-section curve, and a multi-section line, or a combination of the multi-section curve and the multi-section line.
- the plunger sleeve of the high-pressure pump includes a first section and a second section connected to the first section, the protruding member is disposed on the outer side of the second section close to the first section, and the first section is located in the first pressure chamber.
- the position at which the protruding member is in interference fit to the pressure chamber is lower.
- the first section is deformed and shrunk inwards due to the pressure difference between the inside and the outside of the first section, and the clearance between the first section and the plunger is reduced, which effectively reduces the likelihood of backflow through the clearance.
- the high-pressure pump of the present invention has a larger plunger clearance in the fuel sucking stage, less wear to the plunger set, and a longer service life than the existing high-pressure pump. Therefore, it is possible to further reduce the machining clearance in the plunger set to increase the volumetric efficiency, without increasing the weight or using more expensive materials.
- 1' denotes a pressure chamber; 3' denotes a plunger sleeve; 4' denotes a plunger; 5' denotes an inlet valve; 6' denotes an outlet valve; 7' denotes a machining clearance in a plunger set; 8' denotes a protruding member.
- 1 denotes a first pressure chamber
- 2 denotes a second pressure chamber
- 3 denotes a plunger sleeve
- 31 denotes a first section
- 32 denotes a second section
- 4 denotes a plunger
- 5 denotes an inlet valve
- 6 denotes an outlet valve
- 7 denotes a machining clearance in a plunger set
- 8 denotes a protruding member.
- FIGs. 2 and 4 are schematic structural diagrams of a high-pressure pump according to the present invention.
- the high-pressure pump comprises a pressure chamber, a plunger sleeve 3 disposed in the pressure chamber, a protruding member 8 disposed at an outer side of the plunger sleeve 3 and in interference fit to the wall of the pressure chamber, a plunger 4 disposed in the plunger sleeve 3, an inlet valve 5, and an outlet valve 6.
- the plunger sleeve 3 comprises a first section 31 and a second section 32 connected to the first section 31.
- the protruding member 8 is disposed on the outer side of the second section 32 close to the first section 31.
- the protruding member 8 divides the pressure chamber into a first pressure chamber 1 and a second pressure chamber 2.
- the first section 31 is located in the first pressure chamber 1, and the inlet valve 5 and the outlet valve 6 are disposed at the first pressure chamber 1.
- the protruding member serves as a boundary point which divides the pressure chamber into a first pressure chamber 1 and a second pressure chamber 2.
- the protruding member 8 shown in FIG. 2 is at a lower position than the protruding member 8' shown in FIG 1 , so that the plunger sleeve 3 is received in the first pressure chamber with a defined length (i.e., the first section).
- the length of the plunger sleeve received in the first pressure chamber is increased in FIG. 2 , to solve the problem that in the fuel pumping stage of the high-pressure pump, the high-pressure fuel is likely to return to the low-pressure area through the plunger clearance, and the volumetric efficiency is reduced.
- Two stages including a fuel pumping stage and a fuel sucking stage are involved in the operation of the high-pressure pump, which are specified as follows: As shown in FIG. 2 , in the fuel pumping stage, the plunger 4 moves from the second pressure chamber 2 towards the first pressure chamber 1, so that the pressure in the first pressure chamber 1 is higher than that in the second pressure chamber 2. In this case, a pressure difference is generated between the inside and the outside of the first section 31, which means the pressure in the first pressure chamber 1 is progressively decreased along a direction towards the second pressure chamber 2.
- the main reason is that the outer side of the first section 31 of the plunger sleeve 3 is affected by the high and constant pressure in the first pressure chamber 1, and the inner side of the first section 31 of the plunger sleeve 3 is in communication with the second pressure chamber 2, and thus, the pressure at the inner side of the first section 31 of the plunger sleeve 3 is progressively decreased along a direction from the first pressure chamber 1 towards the second pressure chamber 2 and is less than the pressure applied to the outer side of the first section 31.
- the first section 31 is deformed and contracted inwards, so that the clearance between the first section 31 of the plunger sleeve 3 and the plunger 4 is smaller than the machining clearance 7 in the plunger set (i.e., the original machining clearance between the plunger 4 and the plunger sleeve 3).
- the plunger 4 moves from the first pressure chamber 1 towards the second pressure chamber 2, so that the pressure in the first pressure chamber 1 becomes equal to that in the second pressure chamber 2. Therefore, no pressure difference is generated between the inside and the outside of the first section 31, and the first section 31 is recovered to the shape before deformation from the inwardly contracted configuration in the fuel pumping stage, and the clearance between the first section 31 of the plunger sleeve 3 and the plunger 4 is equal to the clearance between the second section 32 of the plunger sleeve 3 and the plunger 4 (i.e., the initial state of the plunger sleeve 3), which are equal to the machining clearance 7 in the plunger set.
- the machining clearance 7 in the plunger set has a width ranging from 1 ⁇ m to 15 ⁇ m.
- the high-pressure pump of the present invention can have a larger plunger clearance in the fuel sucking stage, a less wear to the plunger set, and a longer service life, and can further reduce the machining clearance 7 in the plunger set to increase the volumetric efficiency.
- the machining clearance 7 in the plunger set can be further reduced, to reduce the likelihood of backflow through the clearance, without increasing the weight or using more expensive materials.
- the greater the fuel pumping pressure is the larger the adaptive deformation is, and the more significant the beneficial effects to the volumetric efficiency is, thereby effectively improving the fuel combustion utilization rate and reducing fuel consumption.
- the inner diameter of the first section 31 of the plunger sleeve 3 is the same as that of the second section 32 of the plunger sleeve 3, and the outer diameter of the first section 31 of the plunger sleeve 3 is the same as or different from that of the second section 32 of the plunger sleeve 3.
- the outer diameter of the first section 31 of the plunger sleeve 3 is different from that of the second section 32 of the plunger sleeve 3, so that the first section 31 is more likely to be deformed to contract in the fuel pumping stage.
- the first section is connected to the second section through a transition section which facilitates in mounting the plunger sleeve in the pressure chamber, and the cross section of the transition section is shaped with one of a round corner, a right angle, a chamfer, a multi-section curve, and a multi-section line, or a combination of the multi-section curve and the multi-section line.
- the plunger sleeve of the high-pressure pump includes a first section and a second section connected to the first section, the protruding member is disposed on the outer side of the second section close to the first section, and the first section is located in the first pressure chamber.
- the position at which the protruding member is in interference fit to the pressure chamber is lower.
- the first section is deformed and contracted inwards due to the pressure difference between the inside and the outside of the first section, and the clearance between the first section and the plunger is reduced, which effectively reduces the likelihood of backflow through the clearance.
- the high-pressure pump of the present invention has a larger plunger clearance in the fuel sucking stage, a less wear to the plunger set, and a longer service life than the existing high-pressure pump. Therefore, it is possible to further reduce the machining clearance in the plunger set to increase the volumetric efficiency, without increasing the weight or using more expensive materials.
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- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Details Of Reciprocating Pumps (AREA)
- Fuel-Injection Apparatus (AREA)
- Reciprocating Pumps (AREA)
Description
- The present invention relates to the technical field of fuel injection pumps, and in particular, to a high-pressure pump.
- A high-pressure pump is a critical part of a direct fuel injection engine. As shown in
FIG. 1 , the high-pressure pump includes an inlet valve 5', an outlet valve 6', a pressure chamber 1' disposed between the inlet valve 5' and the outlet valve 6', a plunger sleeve 3' disposed in the pressure chamber 1', a protruding member 8' disposed at one end of the plunger sleeve and at its outer side, and in interference fit to the pressure chamber 1', and a plunger 4' disposed inside the plunger sleeve 3'. Pressure is generated by the movement of the plunger 4' in the pressure chamber 1' to convert low-pressure fuel into high-pressure fuel (having a pressure up to 150 bar or higher). - With the continuous improvement of energy conservation and emission reduction requirements, the design and manufacture of high-pressure pumps also face new challenges: it is required to further increase the fuel pumping pressure (up to 350 bar or higher) in the case of lightweight. However, with the increase of pressure, in the fuel pumping stage, the high-pressure fuel is likely to return to low-pressure areas through plunger clearances (which are the sealing clearances between the plunger and the plunger sleeve). As a result, the volumetric efficiency may be reduced. Such problem is especially obvious in low rev conditions, and thus, the fuel supply capacity in low rev condition has become a choke point to fuel pumps to be designed with higher pressure.
- To solve the foregoing problem, the following schemes are adopted currently:
- 1. a larger fuel pumping volume is selected to compensate for the decrease of volumetric efficiency;
- 2. the length of the plunger clearance is increased to counteract the influence of backflow; and
- 3. the machining clearance (see the reference sign 7' in
FIG. 1 ) in the plunger set (comprising the plunger and the plunger sleeve) is reduced, to counteract the influence of backflow. - The above schemes 1 and 2 are accompanied by the increase in weight and cost, and the
above scheme 3 is accompanied by the risks of accelerated wear to the plunger set and a significant decrease in the service life, and it is required to use the material having better performance in wear resistance or to perform a surface treatment process to acquire a better wear resistance. However, the cost will be increased. -
WO2008086011 discloses a clamping and seal loading technique for securing the plunger sleeve to the pump housing of a single plunger fuel pump. This is achieved by providing a load ring between a sleeve retainer and the sleeve, such that the axial force applied by the retainer during installation and attachment to the plunger bore wall of the housing, is distributed more evenly on the sleeve and the sealing surface of the sleeve against the housing adjacent to the pumping chamber. The even distribution of force minimizes misalignment of the sleeve and thus maintains concentricity between the sleeve and the plunger. - An objective of the present invention is to provide a high-pressure pump to solve the problem in the prior art that in the fuel pumping stage of the high-pressure pump, the high-pressure fuel is likely to return to low-pressure areas through a plunger clearance, and the volumetric efficiency is reduced.
- To solve the foregoing technical problem, the present invention provides a high-pressure pump, comprising: a pressure chamber, a plunger sleeve disposed in the pressure chamber, a protruding member disposed at an outer side of the plunger sleeve and in interference fit to a wall of the pressure chamber, a plunger disposed in the plunger sleeve, an inlet valve, and an outlet valve, wherein the plunger sleeve comprises a first section and a second section connected to the first section; the protruding member is disposed on an outer side of the second section close to the first section; the protruding member divides the pressure chamber into a first pressure chamber and a second pressure chamber, the first section is located in the first pressure chamber, and the inlet valve and the outlet valve are disposed at the first pressure chamber.
- Alternatively, in the high-pressure pump, in a fuel pumping stage of the high-pressure pump, the plunger moves from the second pressure chamber towards the first pressure chamber.
- Alternatively, in the high-pressure pump, in the fuel pumping stage of the high-pressure pump, the first pressure chamber has a pressure higher than a pressure of the second pressure chamber.
- According to the invention, in the high-pressure pump, in the fuel pumping stage of the high-pressure pump, the first section of the plunger sleeve deforms to contract inwards, and a clearance between the first section of the plunger sleeve and the plunger is smaller than a machining clearance of a plunger set.
- Alternatively, in the high-pressure pump, in the fuel pumping stage of the high-pressure pump, the pressure in the first pressure chamber is progressively decreased along a direction towards the second pressure chamber.
- Alternatively, in the high-pressure pump, in a fuel sucking stage of the high-pressure pump, the plunger moves from the first pressure chamber towards the second pressure chamber.
- Alternatively, in the high-pressure pump, in the fuel sucking stage of the high-pressure pump, the first pressure chamber has a pressure equal to a pressure of the second pressure chamber.
- Alternatively, in the high-pressure pump, in the fuel sucking stage of the high-pressure pump, a clearance between the first section of the plunger sleeve and the plunger is equal to a clearance between the second section of the plunger sleeve and the plunger, and the clearance between the second section of the plunger sleeve and the plunger is a machining clearance of a plunger set.
- Alternatively, in the high-pressure pump, the first section of the plunger sleeve has an inner diameter same as an inner diameter of the second section of the plunger sleeve, and the first section of the plunger sleeve has an outer diameter same as an outer diameter of the second section of the plunger sleeve.
- Alternatively, in the high-pressure pump, the first section of the plunger sleeve has an inner diameter same as an inner diameter of the second section of the plunger sleeve, and the first section of the plunger sleeve has an outer diameter different from an outer diameter of the second section of the plunger sleeve.
- According to the invention, in the high-pressure pump, the first section of the plunger sleeve has a length satisfying a relationship with a total length of the plunger sleeve as follows:
- Alternatively, in the high-pressure pump, the inner diameter of the first section of the plunger sleeve, the outer diameter of the first section of the plunger sleeve, and the outer diameter of the second section of the plunger sleeve satisfy the following relationship:
- Alternatively, in the high-pressure pump, the first section is connected to the second section through a transition section, and a cross section of the transition section is shaped with any one of a round corner, a right angle, a chamfer, a multi-section curve, and a multi-section line, or a combination of the multi-section curve and the multi-section line.
- In the high-pressure pump provided by the present invention, the plunger sleeve of the high-pressure pump includes a first section and a second section connected to the first section, the protruding member is disposed on the outer side of the second section close to the first section, and the first section is located in the first pressure chamber. Compared with the prior art, the position at which the protruding member is in interference fit to the pressure chamber is lower. In the fuel pumping stage, the first section is deformed and shrunk inwards due to the pressure difference between the inside and the outside of the first section, and the clearance between the first section and the plunger is reduced, which effectively reduces the likelihood of backflow through the clearance. In the fuel sucking stage, no pressure difference generated between the inside and the outside of the first section, so that the first section is recovered from the contracted configuration to the shape before deformation. Therefore, under the premise of the same volumetric efficiency, the high-pressure pump of the present invention has a larger plunger clearance in the fuel sucking stage, less wear to the plunger set, and a longer service life than the existing high-pressure pump. Therefore, it is possible to further reduce the machining clearance in the plunger set to increase the volumetric efficiency, without increasing the weight or using more expensive materials. The greater the fuel pumping pressure is, the greater the deformation of the first section will be, and also the more significant the beneficial effects to the volumetric efficiency will be.
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FIG. 1 is a schematic structural diagram of a high-pressure pump in the prior art; -
FIG. 2 is a schematic structural diagram of a high-pressure pump in a fuel pumping stage according to an embodiment of the present invention; -
FIG. 3 is a schematic structural diagram of a high-pressure pump in a fuel sucking stage according to an embodiment of the present invention; -
FIG. 4 is a schematic sectional diagram of a plunger sleeve according to an embodiment of the present invention; and -
FIGs. 5a-5f are schematic sectional diagrams showing a transition section between a first section and a second section of a plunger sleeve according to an embodiment of the present invention. - In
FIG. 1 , 1' denotes a pressure chamber; 3' denotes a plunger sleeve; 4' denotes a plunger; 5' denotes an inlet valve; 6' denotes an outlet valve; 7' denotes a machining clearance in a plunger set; 8' denotes a protruding member. - In
FIGs. 2-4 , 1 denotes a first pressure chamber; 2 denotes a second pressure chamber, 3 denotes a plunger sleeve; 31 denotes a first section; 32 denotes a second section; 4 denotes a plunger; 5 denotes an inlet valve; 6 denotes an outlet valve; 7 denotes a machining clearance in a plunger set; 8 denotes a protruding member. - The high-pressure pump proposed by the present invention will be further described in detail below with reference to the accompanying drawings and specific embodiments. Advantages and features of the present invention will be apparent from the description and appended claims below. It should be noted that the drawings are in a very simplified form and use non-precise proportions, and are only intended to conveniently and explicitly assist in describing the objectives of embodiments of the present invention.
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FIGs. 2 and4 are schematic structural diagrams of a high-pressure pump according to the present invention. As shown inFIG. 2 , the high-pressure pump comprises a pressure chamber, aplunger sleeve 3 disposed in the pressure chamber, a protrudingmember 8 disposed at an outer side of theplunger sleeve 3 and in interference fit to the wall of the pressure chamber, aplunger 4 disposed in theplunger sleeve 3, aninlet valve 5, and anoutlet valve 6. Theplunger sleeve 3 comprises afirst section 31 and asecond section 32 connected to thefirst section 31. The protrudingmember 8 is disposed on the outer side of thesecond section 32 close to thefirst section 31. The protrudingmember 8 divides the pressure chamber into a first pressure chamber 1 and a second pressure chamber 2. Thefirst section 31 is located in the first pressure chamber 1, and theinlet valve 5 and theoutlet valve 6 are disposed at the first pressure chamber 1. - The protruding member serves as a boundary point which divides the pressure chamber into a first pressure chamber 1 and a second pressure chamber 2. As shown in
FIGs. 1 and 2 , theprotruding member 8 shown inFIG. 2 is at a lower position than the protruding member 8' shown inFIG 1 , so that theplunger sleeve 3 is received in the first pressure chamber with a defined length (i.e., the first section). In other words, compared with the structure shown inFIG. 1 , the length of the plunger sleeve received in the first pressure chamber is increased inFIG. 2 , to solve the problem that in the fuel pumping stage of the high-pressure pump, the high-pressure fuel is likely to return to the low-pressure area through the plunger clearance, and the volumetric efficiency is reduced. - Two stages including a fuel pumping stage and a fuel sucking stage are involved in the operation of the high-pressure pump, which are specified as follows:
As shown inFIG. 2 , in the fuel pumping stage, theplunger 4 moves from the second pressure chamber 2 towards the first pressure chamber 1, so that the pressure in the first pressure chamber 1 is higher than that in the second pressure chamber 2. In this case, a pressure difference is generated between the inside and the outside of thefirst section 31, which means the pressure in the first pressure chamber 1 is progressively decreased along a direction towards the second pressure chamber 2. The main reason is that the outer side of thefirst section 31 of theplunger sleeve 3 is affected by the high and constant pressure in the first pressure chamber 1, and the inner side of thefirst section 31 of theplunger sleeve 3 is in communication with the second pressure chamber 2, and thus, the pressure at the inner side of thefirst section 31 of theplunger sleeve 3 is progressively decreased along a direction from the first pressure chamber 1 towards the second pressure chamber 2 and is less than the pressure applied to the outer side of thefirst section 31. Under the effect of the pressure difference, thefirst section 31 is deformed and contracted inwards, so that the clearance between thefirst section 31 of theplunger sleeve 3 and theplunger 4 is smaller than themachining clearance 7 in the plunger set (i.e., the original machining clearance between theplunger 4 and the plunger sleeve 3). - As shown in
FIG. 3 , in the fuel sucking stage, theplunger 4 moves from the first pressure chamber 1 towards the second pressure chamber 2, so that the pressure in the first pressure chamber 1 becomes equal to that in the second pressure chamber 2. Therefore, no pressure difference is generated between the inside and the outside of thefirst section 31, and thefirst section 31 is recovered to the shape before deformation from the inwardly contracted configuration in the fuel pumping stage, and the clearance between thefirst section 31 of theplunger sleeve 3 and theplunger 4 is equal to the clearance between thesecond section 32 of theplunger sleeve 3 and the plunger 4 (i.e., the initial state of the plunger sleeve 3), which are equal to themachining clearance 7 in the plunger set. Preferably, themachining clearance 7 in the plunger set has a width ranging from 1 µm to 15 µm. - Therefore, compared with an existing high-pressure plunger having a same plunger clearance in fuel pumping stage (i.e., same volumetric efficiency), the high-pressure pump of the present invention can have a larger plunger clearance in the fuel sucking stage, a less wear to the plunger set, and a longer service life, and can further reduce the
machining clearance 7 in the plunger set to increase the volumetric efficiency. In other words, at the cost of service life, themachining clearance 7 in the plunger set can be further reduced, to reduce the likelihood of backflow through the clearance, without increasing the weight or using more expensive materials. Moreover, the greater the fuel pumping pressure is, the larger the adaptive deformation is, and the more significant the beneficial effects to the volumetric efficiency is, thereby effectively improving the fuel combustion utilization rate and reducing fuel consumption. - Further, the inner diameter of the
first section 31 of theplunger sleeve 3 is the same as that of thesecond section 32 of theplunger sleeve 3, and the outer diameter of thefirst section 31 of theplunger sleeve 3 is the same as or different from that of thesecond section 32 of theplunger sleeve 3. In this embodiment, it is preferable that the outer diameter of thefirst section 31 of theplunger sleeve 3 is different from that of thesecond section 32 of theplunger sleeve 3, so that thefirst section 31 is more likely to be deformed to contract in the fuel pumping stage. - Referring to
FIG. 4 , regardless of whether the outer diameter of thefirst section 31 of theplunger sleeve 3 is the same as that of thesecond section 32 of theplunger sleeve 3, it is necessary to satisfy the following relationship:plunger sleeve 3, and L1 represents the length of thefirst section 31 of theplunger sleeve 3. - Still referring to
FIG. 4 , when the outer diameter of thefirst section 31 of theplunger sleeve 3 is different from that of thesecond section 32 of theplunger sleeve 3, it is necessary to satisfy the following relationship:first section 31 of theplunger sleeve 3, D2 represents the outer diameter of thesecond section 32 of theplunger sleeve 3, and D3 represents the outer diameter of thefirst section 31 of theplunger sleeve 3. - Preferably, referring to
FIGs. 5a-5f , the first section is connected to the second section through a transition section which facilitates in mounting the plunger sleeve in the pressure chamber, and the cross section of the transition section is shaped with one of a round corner, a right angle, a chamfer, a multi-section curve, and a multi-section line, or a combination of the multi-section curve and the multi-section line. - In conclusion, in the high-pressure pump provided by the present invention, the plunger sleeve of the high-pressure pump includes a first section and a second section connected to the first section, the protruding member is disposed on the outer side of the second section close to the first section, and the first section is located in the first pressure chamber. Compared with the prior art, the position at which the protruding member is in interference fit to the pressure chamber is lower. In the fuel pumping stage, the first section is deformed and contracted inwards due to the pressure difference between the inside and the outside of the first section, and the clearance between the first section and the plunger is reduced, which effectively reduces the likelihood of backflow through the clearance. In the fuel sucking stage, no pressure difference is generated between the inside and the outside of the first section, so that the first section is recovered from the contracted state to the shape before deformation. Therefore, under the premise of the same volumetric efficiency, the high-pressure pump of the present invention has a larger plunger clearance in the fuel sucking stage, a less wear to the plunger set, and a longer service life than the existing high-pressure pump. Therefore, it is possible to further reduce the machining clearance in the plunger set to increase the volumetric efficiency, without increasing the weight or using more expensive materials.
Claims (10)
- A high-pressure pump, comprising: a pressure chamber, a plunger sleeve (3) disposed in the pressure chamber, a protruding member (8) disposed at an outer side of the plunger sleeve (3) and in interference fit to a wall of the pressure chamber, a plunger (4) disposed in the plunger (4) sleeve, an inlet valve (5), and an outlet valve (6); wherein the plunger sleeve (3) comprises a first section (31) and a second section (32) connected to the first section (31); the protruding member (8) is disposed on an outer side of the second section (32) close to the first section (31); the protruding member (8) divides the pressure chamber into a first pressure chamber (1) and a second pressure chamber (2), the first section (31) is located in the first pressure chamber (1), and the inlet valve (5) and the outlet valve (6) are disposed at the first pressure chamber (1); in a fuel pumping stage of the high-pressure pump, the plunger (4) moves from the second pressure chamber (2) towards the first pressure chamber (1);wherein the first section (31) of the plunger sleeve (3) has a length satisfying a relationship with a total length of the plunger sleeve (3) as follows:wherein L2 represents the total length of the plunger sleeve (3), and L1 represents the length of the first section (31) of the plunger sleeve (3);wherein in the fuel pumping stage of the high-pressure pump, the first section (31) of the plunger sleeve (3) deforms to contract inwards, and a clearance between the first section (31) of the plunger sleeve (3) and the plunger (4) is smaller than a machining clearance (7) of a plunger set.
- The high-pressure pump according to claim 1, wherein in the fuel pumping stage of the high-pressure pump, the first pressure chamber (1) has a pressure higher than a pressure of the second pressure chamber (2).
- The high-pressure pump according to claim 2, wherein in the fuel pumping stage of the high-pressure pump, the pressure in the first pressure chamber (1) is progressively decreased along a direction towards the second pressure chamber (2).
- The high-pressure pump according to claim 1, wherein in a fuel sucking stage of the high-pressure pump, the plunger (4) moves from the first pressure chamber (1) towards the second pressure chamber (2).
- The high-pressure pump according to claim 4, wherein in the fuel sucking stage of the high-pressure pump, the first pressure chamber (1) has a pressure equal to a pressure of the second pressure chamber (2).
- The high-pressure pump according to claim 5, wherein in the fuel sucking stage of the high-pressure pump, a clearance between the first section (31) of the plunger sleeve (3) and the plunger (4) is equal to a clearance between the second section (32) of the plunger sleeve (3) and the plunger (4), and the clearance between the second section (32) of the plunger sleeve (3) and the plunger (4) is a machining clearance (7) of a plunger set.
- The high-pressure pump according to claim 1, wherein the first section (31) of the plunger sleeve (3) has an inner diameter same as an inner diameter of the second section (32) of the plunger sleeve (3), and the first section (31) of the plunger sleeve (3) has an outer diameter same as an outer diameter of the second section (32) of the plunger sleeve (3).
- The high-pressure pump according to claim 1, wherein the first section (31) of the plunger sleeve (3) has an inner diameter same as an inner diameter of the second section (32) of the plunger sleeve (3), and the first section (31) of the plunger sleeve (3) has an outer diameter different from an outer diameter of the second section (32) of the plunger sleeve (3).
- The high-pressure pump according to claim 8, wherein the inner diameter of the first section (31) of the plunger sleeve (3), the outer diameter of the first section (31) of the plunger sleeve (3), and the outer diameter of the second section (32) of the plunger sleeve (3) satisfy the following relationship:
- The high-pressure pump according to claim 9, wherein the first section (31) is connected to the second section (32) through a transition section, and a cross section of the transition section is shaped with any one of a round corner, a right angle, a chamfer, a multi-section curve, and a multi-section line, or a combination of the multi-section curve and the multi-section line.
Applications Claiming Priority (2)
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CN201710058832.2A CN106762299B (en) | 2017-01-23 | 2017-01-23 | High-pressure pump |
PCT/CN2018/073787 WO2018133876A1 (en) | 2017-01-23 | 2018-01-23 | High-pressure pump |
Publications (3)
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EP3572664A1 EP3572664A1 (en) | 2019-11-27 |
EP3572664A4 EP3572664A4 (en) | 2020-01-01 |
EP3572664B1 true EP3572664B1 (en) | 2022-05-18 |
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EP18741821.5A Active EP3572664B1 (en) | 2017-01-23 | 2018-01-23 | High-pressure pump |
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EP (1) | EP3572664B1 (en) |
CN (1) | CN106762299B (en) |
WO (1) | WO2018133876A1 (en) |
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CN106762299B (en) * | 2017-01-23 | 2023-06-20 | 联合汽车电子有限公司 | High-pressure pump |
Citations (1)
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WO2008086011A2 (en) * | 2007-01-10 | 2008-07-17 | Stanadyne Corporation | Load ring mounting of pumping plunger |
Family Cites Families (11)
Publication number | Priority date | Publication date | Assignee | Title |
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JPH07217742A (en) * | 1993-12-10 | 1995-08-15 | Kayaba Ind Co Ltd | Bushing mounting method |
JP3652005B2 (en) * | 1996-03-27 | 2005-05-25 | カヤバ工業株式会社 | How to install the bush |
DE102004063074B4 (en) * | 2004-12-28 | 2013-03-07 | Robert Bosch Gmbh | Piston pump, in particular high-pressure fuel pump for an internal combustion engine |
DE102008040090A1 (en) * | 2008-07-02 | 2010-01-07 | Robert Bosch Gmbh | High-pressure pump, particularly radial piston pump or in-line piston pump for fuel injection system of air-compressing, self-ignited internal combustion engine, comprises housing, drive shaft stored in housing, and cylinder head |
CN102619660B (en) * | 2011-01-28 | 2015-06-24 | 株式会社电装 | High pressure pump |
WO2015032558A1 (en) * | 2013-09-04 | 2015-03-12 | Continental Automotive Gmbh | High pressure pump |
JP6368517B2 (en) * | 2014-03-28 | 2018-08-01 | Kyb株式会社 | Hydraulic rotating machine |
CN204458157U (en) * | 2015-03-02 | 2015-07-08 | 北京博曼迪汽车科技有限公司 | High-pressure common-rail oil pump and plunger coupled parts device thereof |
CN205225549U (en) * | 2015-12-02 | 2016-05-11 | 无锡威孚马山油泵油嘴有限公司 | Novel plunger matching parts |
CN106762299B (en) * | 2017-01-23 | 2023-06-20 | 联合汽车电子有限公司 | High-pressure pump |
CN206439132U (en) * | 2017-01-23 | 2017-08-25 | 联合汽车电子有限公司 | High-pressure pump |
-
2017
- 2017-01-23 CN CN201710058832.2A patent/CN106762299B/en active Active
-
2018
- 2018-01-23 WO PCT/CN2018/073787 patent/WO2018133876A1/en active Application Filing
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WO2008086011A2 (en) * | 2007-01-10 | 2008-07-17 | Stanadyne Corporation | Load ring mounting of pumping plunger |
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Publication number | Publication date |
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CN106762299B (en) | 2023-06-20 |
EP3572664A1 (en) | 2019-11-27 |
WO2018133876A1 (en) | 2018-07-26 |
CN106762299A (en) | 2017-05-31 |
EP3572664A4 (en) | 2020-01-01 |
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