Abstract:
A poppet valve device is composed such that a plurality of axial passages of substantially the same diameter and length communicating to a high-pressure space formed inside the valve seat member between the poppet valve body and the valve seat member are provided in the valve seat member. The passages are located adjacent to each other, or located axially symmetrically. An annular gap formed between the periphery of the poppet valve body and the inner perimeter of a projecting part on which the valve seat face of the valve seat member is formed is narrow to restrict liquid flow through the annular gap. An electronic controlled fuel injection apparatus equipped with the poppet valve device is composed such that a lower end part of the poppet valve body and the bottom of a valve device accommodating part of the fuel injection apparatus are formed to restrict the flow of fuel from between the lower end of the poppet valve body and the bottom of the valve device accommodation part to the central hollow of the poppet valve body, whereby the occurrence of bouncing is prevented.

Description:
BACKGROUND OF THE INVENTION 
   1. Field of the Invention 
   The present invention relates to a poppet valve device for performing opening and closing of a high-pressure liquid passage, specifically to a poppet valve device to control the injection timing of an electronic controlled fuel injection apparatus for an internal combustion engine. 
   2. Description of the Related Art 
   In diesel engines, electronic controlled fuel injection apparatus have been widely used recently as an effective means for reducing atmospheric pollutants such as NOx (nitrogen oxides) and HC (hydrocarbons) (for example, see Japanese Laid-Open Patent Application Nos 2001-248479 and 2002-98024). 
   A poppet valve device driven by an electromagnetic valve device is used in each of these apparatuses for opening and closing the fuel passage in the apparatus. 
     FIG. 6  represents an example of a unit injector type electronic controlled fuel injection apparatus for a diesel engine. The unit injector like this is well known in the art and here brief explanation will be given. In the drawing, reference numeral  100  comprises a fuel injection pump part  101  and a fuel injection nozzle part  102 . The fuel injection pump part  101  includes a poppet valve  5  and an electromagnetic valve device  20  for opening and closing the valve. A plunger  1  fitted into a pump case  3  is driven to reciprocate by way of a tappet  6 , contact piece  7 , plunger spring  8 , etc. by means of a rocker arm  54  which is driven mechanically by the engine crank shaft to oscillate. A plunger chamber  25  is communicated to the injection nozzle part  102  via a fuel passage  052  on one side and communicated to the poppet valve  5  via a fuel passage  52  on the other side. The fuel passage  52  is communicated or discommunicated to a fuel passage  12  connecting to a fuel tank (not shown in the drawing) by opening or closing of the poppet valve  5 , which is opened or closed by the electromagnetic valve device  20 . The fuel injection nozzle part  102  includes a fuel injection nozzle  2  and a needle valve spring  51 . The fuel pushed by a plunger  1  to be compressed in the plunger chamber  25  flows through the fuel passage  052  to a fuel pool  02  and is injected from the injection holes  02   a.    
   When the poppet valve  5  is opened, the pressure in the plunger chamber  25  does not increase by a down stroke of the plunger  1  because the plunger chamber  25  is communicated to the fuel tank through the fuel passage  52 , through the poppet valve, and through the fuel passage  12 . When the poppet valve  5  is closed, the pressure in the plunger chamber  25  increases as the plunger  1  moves down, and when the pressure in the fuel pool  02  reaches the needle-opening pressure, the needle valve  4  lifts up, overcoming the spring force of the needle valve spring  51 , and the fuel begins to be injected from the injection holes  02   a.  During the fuel injection period, the amount of fuel compressed by the plunger is larger than that injected from the injection holes  02   a  of the injection nozzle  2  and the injection pressure increases with time. When the poppet valve is opened to communicate the plunger chamber  25  to the fuel tank, the pressure in the plunger chamber decreases rapidly, the pressure in the fuel pool  02  decreases rapidly, the needle valve is pushed down by the spring force of the needle valve spring  51  for the needle valve to be closed, and the injection is finished. In the succeeding lifting stroke of the plunger, fuel is sucked into the plunger chamber  25  through the fuel passage  12 , poppet valve  5 , and fuel passage  52 . 
   An example of the conventional poppet valve used in an electronic controlled fuel injection apparatus for the purpose as above described is shown in  FIG. 7(A)  and  FIG. 7(B)  together with an electromagnetic valve.  FIG. 7(A)  shows the state in which the popped valve is opened, and  FIG. 7(B)  shows the state in which the poppet valve is closed. In the drawings, reference numeral  20  is an electromagnetic valve device,  3  is the pump case of a unit injector as explained above, and  52  is the fuel passage communicating to the plunger chamber of the unit injector. In the electromagnetic valve device  20 , reference numerals  31  and  16  are valve cases,  031  is a solenoid housing inside the valve case  31 , and  28  is a solenoid accommodated in the solenoid housing  031 . 
   In an armature space  30 , an armature  27  is fixed to the top of the poppet valve  5  by means of a bolt  29 . 
   Reference numeral  10  is a valve seat member fixed in the pump case  3  by means of a fixing screw member  015 . Reference numeral  033  is a passage hole drilled in the valve seat member  10  in the radial direction which allows an annular recess  05  of the poppet valve to communicate to an annular recess  17  of valve seat member  10 . The recesses  05  and  17  are explained later. Reference numeral  5  is the poppet valve, which is fit in a through-hole of the valve seat member  10  for sliding and to the top of which is fixed the armature  27  by means of the bolt  29 . Reference numeral  14  is a poppet valve spring disposed between the shoulder part of the poppet valve  5  and the ceiling part of the fixing screw member  015 . The poppet valve  5  is pushed downward in the direction for the poppet valve  5  to be opened, that is, in the reverse direction of the attraction force of the armature  27 . Reference numeral  05  is the annular recess formed along the periphery of the poppet valve  5 , and reference numeral  17  is the annular recess formed along the periphery of the valve seat member  10 . Reference numeral  12  is the supply and drain passage, one side thereof communicating to the annular recess  17  and the other side being connected to a fuel tank (not shown in the drawings). Reference numeral  10   a  is a seat face in the valve seat member  10  and  5   a  is a seat face of the poppet valve  5 . The seat face  5   a  of the poppet valve sits on the seat face  10   a  of the valve seat member when closing the poppet valve. Accordingly, as the seat face  5   a  sits on or departs from the seat face  10   a  of the valve seat member  10 , supply and drain passage  12  is discommunicated or communicated to the fuel passage  52  in the pump case  3 . Reference numeral  07  is an axial passage communicating to an annular recess  06  formed along the inside circumference of the valve seat member  10 , the axial passage  07  communicating to the fuel passage  52  which communicates to the plunger chamber of an injection pump not shown in  FIG. 7(A)  and  FIG. 7(B) . When the poppet valve  5  is closed, the fuel pressure is high in the recess  06  and low in the recess  05 . 
   When electric current is shut off from flowing to the solenoid  28  of the electromagnetic valve device  20 , the poppet valve  5  is pushed down by the spring force of the poppet valve spring  14 , a gap “S” is developed between the upper surface of the armature  27  and the lower surface of the solenoid  28 , the lower end face  5   b  of the poppet valve  5  contacts the bottom face  3   a  of the poppet valve device accommodating part of the pump case, the seat face  5   a  of the poppet valve  5  departs from the seat face  10   a  of the valve seat member  10 , and the poppet valve is opened. Therefore, the plunger chamber  25  (see  FIG. 6 ) is communicated to the supply and drain passage  12  through the fuel passage  52 , the gap between the seat faces  5   a  and  10   a  developed by the departing of the seat face  5   a  from the seat face  10   a,  the passage hole  033  of the valve seat member  10 , and the annular recess  17 , and the fuel pushed down in the plunger chamber  25  as the plunger  1  (see  FIG. 6 ) moves down is returned to the fuel tank via the fuel supply and drain pipe  12 . Accordingly, fuel is not injected by the down stroke of the plunger  1 . 
   When electric current flows to the solenoid  28  of the electromagnetic valve device  20 , the armature  27  and the poppet valve  5  connected thereto are lifted up by the attraction generated in the solenoid  28  against the spring force of the valve seat spring  14  until the seat face  5   a  of the poppet valve  5  sits on the seat face  10   a  of the valve seat member  10 , and the poppet valve is closed. Then the pressure rises in the plunger chamber  25  as the plunger  1  moves down, and the fuel pushed out from the plunger chamber  25  is injected from the injection holes  02   a  of the injection nozzle  2 . 
   In recent years, the injection pressure is increasingly apt to be increased in order to enhance the effect of an electronic fuel injection apparatus to reduce atmospheric contaminants such as NOx and HC. The poppet valve device working in the electronic fuel injection apparatus as described above will be brought under more severe working conditions as fuel injection pressure increases. 
   However, with the poppet valve device of the prior art, there are problems in that cavitation erosion occurs in the poppet valve body and valve seat member due to the outburst of high-pressure fuel through the gap of the valve seat part, friction of sliding of the poppet valve body increases due to increased side thrust exerted on the poppet valve body, a crack occurs in the passage exposed to high-pressure liquid in the valve device and that bouncing occurs when the poppet valve opens, that is, when the seat face of the poppet valve body departs from the seat face of the valve seat member and the lower end face of the poppet valve contacts the bottom face of the poppet valve device accommodating part of the injection pump case. 
   SUMMARY OF THE INVENTION 
   The present invention was made in light of the problems as above described, and the object is to provide a poppet valve device with which the occurrence of a crack in the passage exposed to high-pressure liquid in the valve device, occurrence of cavitation erosion in the poppet valve body and valve seat member of the valve device, increase in sliding friction of the poppet valve body, and the occurrence of bouncing of the poppet valve body can be prevented. 
   To solve these problems, the present invention proposes a poppet valve device for opening and closing a high-pressure liquid passage comprising a valve seat member and a poppet valve body inserted in the through-hole of the valve seat member for sliding where the device is composed such that the seating of the seat face of the poppet valve body onto the seat face of the valve seat member separates an annular, high-pressure space from an annular, low-pressure space. The annular spaces are formed between the poppet valve body and the valve seat member. The valve seat member has an axial passage communicating to the high-pressure space and a radial passage communicating to the low-pressure space. The axial passage is formed into a plurality of passages of substantially the same diameter and length located adjacent to each other. 
   In the poppet valve device, the high-pressure space is not always exposed to high pressure liquid, but temporarily, and the axial passage communicating to the high-pressure space is exposed to the repetition of high pressure and low pressure. Conventionally, one axial passage has been provided in the valve seat member, and the radial thickness between the periphery of the trough-hole (hereafter referred to as the sliding surface) and the periphery of the axial passage is inevitably limited due to space limitations; when the valve device was used for high-pressure injection apparatus, the part having the limited radial thickness cracked. 
   By providing a plurality of axial passages having a required passage area, the stress due to high pressure in the passages is dispersed and reduced. Therefore, cracks do not occur even if the thickness between the sliding surface and the periphery of the axial passage are the same as that in the case of the conventional one axial passage. Further, as the diameter of each of the passages is reduced, the outer diameter of the annular, high-pressure space can be reduced. As a result, it is possible to design toward reducing the volume of the high-pressure space. 
   To reduce the volume of high pressure space means that dead volume is reduced, which results in a sharp rise of injection pressure in the case of a fuel injection apparatus, for example. That is, as the rate of rise of the pressure of the fuel compressed by the plunger is reduced less with a smaller dead volume, the injection pressure rises faster with the same plunger diameter and the same plunger velocity. 
   Further, in the present invention, it is preferable that the axial passage is formed into a plurality of passages of substantially same diameter and length located axially symmetrically to the center axis of the valve device. 
   When the valve is closed, the poppet valve body experiences even pressure around its periphery from the liquid filling the high-pressure space. When valve is opened, the liquid in the high-pressure space flows out into the low-pressure space and high-pressure liquid flows into the high-pressure space through the axial passage. When one axial passage is provided, the high-pressure liquid flow entering into the high-pressure space through the axial passage acts to push the poppet valve body, and a side thrust exerts on the sliding part of the poppet valve body and the through-hole of the valve seat member. Therefore, the resistance for the poppet valve body to slide is caused, which increases with increased liquid pressure in the axial passage. Further, the flow velocity in the annular gap between the seat faces is faster near the axial passage in the annular gap and slower at the part opposite to the axial passage. The uneven velocity distribution in the annual gap between the seat faces induces a decrease in discharge coefficient and an increase in pressure loss. 
   By providing a plurality of axial passages of substantially the same diameter and length located in axial symmetry, the thrusts exerted on the poppet valve body are balanced because the high-pressure liquid enters into the high-pressure space axially symmetrically, no resultant thrust exerts on the poppet valve body, and a result poppet valve body can move smoothly. Further, as a plurality of axial passages are provided, the velocity distribution of flow in the gap between the seat faces approaches a more even distribution along the annular gap, and the maximum velocity decreases with the required flow rate through the gap secured. By this, the occurrence of cavitation erosion on the poppet valve body and valve seat member can be suppressed. 
   In the present invention, it is preferable that the radial width of the annular gap formed between the periphery of the poppet valve body in the middle part thereof and the inside perimeter of an annular projection of the valve seat member is narrowed to restrict liquid flow from the high-pressure space to the low-pressure space so that the occurrence of cavitation erosion is suppressed. 
   When the poppet valve opens, the liquid in the high-pressure space bursts out rapidly to the low-pressure space and cavitation bubbles are generated. Cavitation erosion occurs on the surface of the poppet valve body and valve seat member by the liquid hammer action induced by the extinction of the bubbles. 
   According to the invention, as the radial width of the annular gap connecting the high-pressure space to the low-pressure space is restricted, the velocity distribution in the annual gap between the seat faces is made more uniform, resulting in a reduced maximum flow velocity when the seat face of the poppet valve body departs from the seat face of the valve seat member and liquid flows out from the high-pressure space to the low-pressure space passing through the annular gap between the seat faces; the energy of the liquid flow passing through the annular gap between the seat faces and colliding against the poppet valve body is suppressed so that the occurrence of cavitation erosion is suppressed. 
   Further, the present invention proposes an electronic controlled fuel injection apparatus provided with the poppet valve device, wherein a valve seat member of the poppet valve device is fixed to a valve device accommodating part so that the bottom end of the valve seat member is in close contact with the bottom face of the valve device accommodating part. The poppet valve body of the valve device is forced by an elastic member in the direction the seat face of the poppet valve body departs from the seat face of the valve seat member. The electromagnetic valve device is provided so that the poppet valve is closed when the poppet valve body is attracted by the electromagnetic valve device against the elastic force of the said elastic member to allow the seat face of the poppet valve body to sit on the seat face of the valve seat member and the poppet valve is opened when the attraction of the electromagnetic valve device is released to allow the seat face of the poppet valve body to depart from the seat face of the valve seat member. The electronic controlled fuel injection apparatus is characterized by the poppet valve device of the invention being mounted with the configuration of valve device mounting part being the same as in the prior art. 
   It is preferable that the poppet valve body of the valve device has a central hollow for allowing the fuel leaked from the sliding part of the poppet valve body in the through-hole of the valve seat member to escape to the poppet valve spring accommodating space. A cylindrical projection is formed on the bottom of the valve device accommodating part so that the cylindrical projection can fit in the central hollow of the poppet valve body with a small radial clearance. The impact when the lower end face of the poppet valve body collides against the bottom face of the valve device accommodating part is lessened and the occurrence of bouncing of the poppet valve body is prevented. 
   In an electronic fuel injection apparatus, a poppet valve device is provided for controlling fuel injection timing in the fuel supply line of the apparatus to supply fuel to the fuel injection pump of the apparatus. The timing of opening and closing of the valve device is electronically controlled by means of an electromagnetic valve device and an elastic member (usually a coil spring). 
   The valve is closed by lifting the poppet valve body by the attraction of the electromagnetic valve device and opened by pushing down the poppet valve body by the spring force of the poppet valve spring until the lower end face of the poppet valve body is brought into contact with the bottom face of the valve device accommodating part of the injection pump case. When the valve is closed, there is formed a clearance between the lower end face of the poppet valve body and the bottom face of the valve device accommodating part. The clearance is filled with the fuel leaked from the sliding part of the of the poppet valve body in the through-hole of the valve seat member, so the fuel in the clearance must be exhausted from there in order to allow the lower end face of the poppet valve body to come into contact with the bottom face of the valve device accommodating part. 
   For this purpose, an escape hole for letting out the fuel to the space where the poppet valve spring is accommodated is provided in the poppet valve body. By providing a cylindrical projection on the bottom of the valve device accommodating part to fit into the escape hole with small radial clearance to form an annular clearance of small radial width when the poppet valve body comes down, the fuel in the clearance between the lower end face of the poppet valve body and the bottom face of the valve device accommodating part must pass through the annular clearance to escape through the escape hole, by which resistance is caused for the poppet valve body to move down. The impact when the lower end face of the poppet valve body collides against the bottom of the valve device accommodating part is thus lessened. 
   If the height of the cylindrical projection is formed to be larger than the lift of the poppet valve body, the resistance due to fuel escape flow restriction acts during the entire period the poppet valve body moves down, and if the height is smaller than the lift of the poppet valve body, the resistance due to fuel escape flow restriction acts just before the lower end of the poppet valve body reaches the bottom of the valve device accommodating part. Thereby both good responsiveness of valve opening and lessening of the impact can be secured, where good responsiveness means that fuel injection ends sharply. 
   By softening the impact, valve bouncing, in which the poppet valve body collides against the bottom of the valve device accommodating part and rebounds from the bottom, is prevented. It is required to prevent bouncing because the bouncing of the poppet valve body causes pressure oscillation in the high-pressure passage between the valve device and the injection nozzle, which deteriorates the sharpness of injection end, resulting in reduced engine performance. 
   In the present invention, it is suitable that the poppet valve body has a cylindrical projection smaller in diameter than that of the sliding part thereof at the lower end part thereof. A cylindrical recess is provided in the bottom of the valve device accommodating part so that the cylindrical projection can fit into the cylindrical recess with a small radial clearance to form an annular gap of small radial width when the poppet valve body moves down for opening the valve until the lower end face thereof comes into contact with the bottom face of the valve device accommodating part. Thereby the impact when the lower end face of the poppet valve body collides against the bottom face of the device accommodating part is lessened and the occurrence of bouncing of the poppet valve body is prevented. 
   It is also preferable that the poppet valve body is provided with a throttling member to throttle fuel flow into the central hollow of the poppet valve body, whereby the impact when the lower end face of the poppet valve body collides against the bottom face of the device accommodating part is lessened and the occurrence of bouncing of the poppet valve body is prevented. 
   In this case, if the throttling hole of the throttling member is formed such that the upper (central hollow side) edge thereof is rounded or chamfered and the lower edge is not rounded or chamfered, the poppet valve body is easy to move upward and downward movement thereof is suppressed. Therefore, by properly rounding or chamfering the upper edge of the throttling hole, bouncing when valve closing and when valve opening can be properly controlled. 

   
     BRIEF DESCRIPTION OF THE DRAWINGS 
       FIG. 1(A)  is a sectional view of a first embodiment of a poppet valve device according to the present invention. 
       FIG. 1(B)  is an enlarged detail of part X in  FIG. 1A  and shown in comparison with the case of the prior art. 
       FIG. 1(C)  is a section along line Y-Y in  FIG. 1(B)  and the case of the present invention compared with the case of prior art. 
       FIG. 2  is a sectional view of a second embodiment of the poppet valve device according to the present invention. 
       FIG. 3  is a sectional view of a third embodiment of the poppet valve device according to the present invention. 
       FIG. 4(A) ,  FIG. 4(B) , and  FIG. 4(C)  are sectional views of a fourth embodiment and modified embodiments thereof of the poppet valve device according to the present invention. 
       FIG. 5  is a graph showing the bouncing of the poppet valve. 
       FIG. 6  is a schematic representation of a unit injector type electronic fuel injection apparatus for a diesel engine. 
       FIG. 7(A)  is a sectional view of a poppet valve device of the prior art showing a state in which the valve is opened. 
       FIG. 7(B)  is a sectional view of a poppet valve device of prior art showing a state in which the valve is closed. 
   

   DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS 
   A preferred embodiment of the present invention will now be detailed with reference to the accompanying drawings. It is intended, however, that unless particularly specified, dimensions, materials, relative positions and so forth of the constituent parts in the embodiments shall be interpreted as illustrative only and not as limitative of the scope of the present invention. 
   [The First Embodiment] 
     FIG. 1(A)  is a sectional view of a first embodiment of the poppet valve device according to the present invention,  FIG. 1(B)  is an enlarged detail of part X in  FIG. 1(A)  and shown in comparison with the case of the prior art, and  FIG. 1(C)  is a section along line Y-Y in  FIG. 1(B)  and the case of present invention compared with the case of the prior art. 
   In  FIG. 1(A) , a poppet valve device  01  consists of a poppet valve body  5  and valve seat member  10 . Reference numeral  05  is a low-pressure space,  06  is a high-pressure space,  07  is an axial passage connecting to the high-pressure space  06 , and  033  are radial passages connecting to the low-pressure space  05 . These reference numerals are the same as those of the poppet valve device in  FIG. 7 . Arrows in  FIG. 1(B)  show the state that fuel pressure is creating in the high-pressure space  06 . 
   In  FIG. 1(C) , a case in which the axial passage  07  consists of two passages each having diameter d 1  is compared with the case in which the axial passage  07  is one passage of diameter of d 0 . The area of the two passages of diameter d 1  is equal to the area of the one passage of diameter of d 0  in the drawing. In the case of the one passage of diameter of d 0 , a maximum tensile stress occurs at E, and a crack occurs when the fuel pressure is high in the passage. In the case of the two passages of diameter of d 1 , the maximum tensile stress occurs at F for each passage, however the tensile stress is smaller, because the diameter of the passage is smaller. 
   In addition, between the two passages of diameter of d 1 , the tensile stress at F is reduced because the circumferential deformation due to the pressure in the two passages cancel each other. 
   As shown in  FIG. 1(B) , the diameter D 1  of the annular high-pressure space  06  can be reduced when the diameter of the axial passage  07  is d 1  in comparison with the case when the diameter of the axial passage  07  is d 0 . Therefore, the volume of the high-pressure space  06  can be reduced. In  FIG. 1(B)  is shown the case two axial passages are provided, however, above mentioned effect is further enhanced by reducing the diameter of the axial passage with increased number of the axial passages. 
   It will be appreciated that in operation, when the poppet valve body  5  moves downward to communicate the annular high-pressure space  06  with the annular low pressure space  05 , a seat face of the poppet valve body unseats from valve seat face  10   a  of the valve seat member  10 . An annular gap is formed between the valve seat face and the seat face of the poppet valve body. This annular gap is formed at an outer periphery side of the poppet valve body. In other words, there is a radial gap from the outermost peripheral surface of the poppet valve body and the valve seat face  10   a  (see e.g. the open position illustrated in  FIG. 2 ). The annular gap is positioned, thus, downstream from the discharge ends of the axial passage  07  such that flow from the axial passages  07  is directed toward the annular gap. 
   [The Second Embodiment] 
     FIG. 2  is a sectional view of a second embodiment of the poppet valve device according to the present invention. In the drawing, two axial passages  07  to the right and left are provided. Other than this point, the poppet valve device of  FIG. 2  is configured similar to that of  FIG. 1(A) , and the same reference numerals are used for components and function parts the same or similar to those of  FIG. 1(A) . In this case, as the high-pressure liquid flows into the high-pressure space  06  through the right and left axial passages  07  at the same time, the poppet valve body  5  experiences pressure from the high-pressure liquid flow at the same time from the right and left, and the poppet valve body  5  does not experience a side thrust as in the case of only one axial passage being provided. 
   Therefore, an increase of friction due to a side thrust when the poppet valve body slides in the valve seat member  10  can be prevented. 
   When the valve opens, the liquid in the high-pressure space  06  flows out to the low-pressure space  05 , passing through the annular gap developed between the seat face  5   a  of the poppet valve body  5  and the seat face  10   a  of the valve seat member  10  as indicated by arrows in  FIG. 2 . Because the high-pressure liquid flows in the high-pressure space  06  through the axial passage or passages, the liquid flow into the low-pressure space tends to become strong in the part of the annular gap between the seat faces nearest to the axial passage or passages, and the velocity of the flow is largest at that part. As two right and left axial passages are provided in the case of  FIG. 2 , the amount of liquid flow per one passage is halved in comparison with the case where only one axial passage is provided, and the collision energy of the liquid flow impinging against the poppet valve body is dispersed into two portions. 
   Therefore, the occurrence of cavitation erosion is prevented or moderated. Two right and left axial passages are provided in  FIG. 2 , however, if a plurality of axial passages more than two are provided in axial symmetry, the effect is further enhanced. 
   [The Third Embodiment] 
     FIG. 3  is a sectional view of a third embodiment of the poppet valve device according to the present invention, and the same reference numerals are used for components and functional parts the same or similar to those of  FIG. 1(A) . A point different from the poppet valve device of  FIG. 1(A)  is that the width “s” of the annular gap between a periphery  5   c  of the middle part of the poppet valve body  5  and the inside perimeter of an annular projection  10   b  of the valve seat member  10  for forming the valve seat  10   a  is narrowed to throttle the liquid flow. 
   When the seat face  5   a  of the poppet valve body  5  departs from the seat  10   a  of the valve seat member  10  and a gap is developed between the seat faces, high-pressure liquid flows out from the high-pressure space  06  to the low-pressure space  05  passing through the gap between the seat faces and further passing through said annular gap of width “s”. When the annular gap of width “s” is narrowed, the flow through the annular gap is restricted by the narrow annular gap, and the flow energy of the liquid is also restricted, so that the collision energy of the liquid flow impinging against the periphery  5   c  of the middle part of the poppet valve body  5  is also restricted. 
   Therefore, the occurrence of cavitation erosion is prevented or moderated. However, if the flow through the annular gap is excessively restricted, the velocity of pressure drop of the high-pressure fuel in the injection pump becomes slower, which results in poor sharpness of injection end. Therefore, the width “s” of the annular gap must be determined so as to be not too small. 
   In the poppet valve devices of the prior art, such a consideration as to provide a throttled part as mentioned above has not been made heretofore. 
   [The Fourth Embodiment and Its Modified Embodiments] 
     FIG. 4(A) ,  FIG. 4(B) , and  FIG. 4(C)  show the fourth embodiment and its modified embodiments, in which each gives a similar effect. 
   In  FIG. 4(A)  and  FIG. 4(B) , the poppet valve device is shown in a state in which the lower end face of the valve seat member  10  contacts the bottom  3   a  of the poppet valve device accommodating part of the fuel injection apparatus. In the drawings, the same reference numerals are used for components and functional parts the same as or similar to those of  FIG. 1(A) , and explanation is omitted. Although the lower end part of the poppet valve body  5  and shape of the bottom face  3   a  of the poppet valve device accommodating part is different in each of  FIGS. 4(A) , (B), and (C), the same reference numerals are used for convenience&#39;s sake. 
   Generally, bouncing occurs when the poppet valve opens, that is, when the poppet valve body  5  is pushed down by the spring force until the lower end face  5   b  thereof impacts upon the bottom face  3   a  of the valve device accommodating part and then rebounds. The bouncing state is shown in  FIG. 5 . The embodiments of  FIG. 4(A)  to  FIG. 4(C)  are configured to prevent the occurrence of bouncing or alleviate bouncing by lessening the impact when the poppet valve body  5  hits the bottom  3   a.    
   The poppet valve body  5  is provided with a central hollow  115  and lateral holes  116  as shown in  FIG. 4(A)  to  FIG. 4(C)  to allow the fuel between the lower end face  5   b  of the poppet valve body and the bottom face  3   a  of the valve device accommodating part to escape through them when the poppet valve body  5  moves down and collides with the bottom face  3   a.  In the embodiment of  FIG. 4(A) , a cylindrical projection  103  is formed on the bottom  3   a  of the valve device accommodating part and the central hollow  115  of the poppet valve body  5  is enlarged in diameter at the lower end part thereof to form an enlarged hole  117  so that the cylindrical projection  103  fits into the enlarged hole  117  with a small radial clearance to form an annular clearance of small radial width when the poppet valve body  5  moves down until the lower end face  5   b  comes into contact with the bottom face  3   a.    
   Therefore, when the poppet valve body  5  moves down, the fuel between the lower end face  5   b  thereof and the bottom face  3   a  of the valve device accommodating part escapes toward the central hollow  115  passing through the narrow annular clearance. 
   Accordingly, there occurs resistance for the poppet valve body to move down, the descending velocity thereof is reduced, and the impact that occurs when the lower end face  5   a  of the poppet valve body collides with the bottom face  3   a  of the valve device accommodating part is lessened. The diameter of the cylindrical projection  103  and enlarged hole should be determined such that the descending velocity is not excessively reduced. The velocity which the gap between the valve seat faces increases is reduced by the reduction in the descending velocity of the poppet valve body, therefore, the energy of fuel flow through the gap between the valve seat faces is reduced, which reduces the potential for cavitation erosion. 
   In the embodiment of  FIG. 4(B) , a cylindrical recess  104  is formed in the bottom face  3   a  of the valve device accommodating part and a cylindrical projection  118  is provided at the lower end part of the poppet valve body  5  so that the cylindrical projection  118  fits into the cylindrical recess  104  with small radial clearance to form an annular gap of small radial width when the poppet valve body  5  moves down until the lower end face  5   b  contacts the bottom face  3   a.  The operation and effect of this embodiment are similar to those of the embodiment of  FIG. 4(A) . 
   In the embodiment of  FIG. 4(C) , an orifice  105  having a small hole  106  is attached to the lower end part of the central hole  115  of the poppet valve body  5 , and the operation and effect of this embodiment are similar to those of the embodiment of  FIG. 4(A) . 
   As has been described in the foregoing, the poppet valve device according to the invention can prevent the occurrence of damage in a high-pressure liquid passage of the valve device, an increase in sliding friction due to the occurrence of a side thrust, the occurrence of cavitation erosion, and the occurrence of bouncing even when the valve device is applied to open and close a passage exposed to high-pressure liquid. Particularly, when the valve device is used for an electronic controlled fuel injection apparatus, an electronic controlled fuel injection apparatus superior in durability can be obtained without using material higher in grade than that used conventionally.