Abstract: A fuel supply pump with a large fuel discharge amount and a tappet structure body, which are suitably used for an accumulated pressure-type fuel injection device that mechanically amplifies pressure, is provided. A fuel supply pump has a tappet structural body and a spring sheet, wherein a penetration portion for allowing passage of a lubricant or a fuel for lubrication therethrough by coordinating the tappet structure and the spring sheet is provided between a spring-holding chamber for holding a spring to be used for pulling up a plunger and a cam chamber for housing a cam to be used for moving the plunger up and down.

Abstract: In a method for driving a solenoid proportional control valve (44) used for flow rate control of a common rail system pump adapted to regulate flow rate by regulating the duty ratio of a pulse voltage applied to a solenoid coil (F) of a solenoid (44E), when an operating condition liable to cause hysteresis in the operation of the solenoid proportional control valve (44) is present, the peak value or pulse width of the pulse voltage is temporarily increased to instantaneously boost the driving force of the solenoid (44E), thereby ensuring smooth operation of a piston (44C) and stabilizing the flow rate control.

Abstract: In order to calculate an estimation of the quantity of accumulated particulates in a filter (32), a first estimation calculation unit (100) that outputs first estimation data (XA) calculated from the filter before and after differential pressure, and a second estimation calculation unit (110) that outputs second estimation data (XB) based on the engine operation status. Of the first and second estimation data (XA, XB), the estimation data having the higher dependability, as viewed from the engine speed at that time, is selected, whether or not to regenerate the filter is determined and with the differential between the first and second estimation (XA, XB) also taken into consideration, when the differential is larger than a prescribed value, even if the engine speed is high, the first estimation data XA is not selected since there is a risk that the dependability of the estimation value is low due to cracking of the accumulated particulates.

Abstract: An existing diesel engine vehicle of light oil fuel is enabled to run as a diesel engine vehicle using DME as fuel without exchanging a whole diesel engine and at very low cost and easily. The shape of a tip part 21 of a needle valve 2 is set by a center diameter L3 for regulating a minimum flow path area at full lift of a fuel injection nozzle 1, a seat diameter L2 of a seat part 211 coming in contact with a valve seat part 33 and blocking communication with a fuel injection hole 31, and a shaft diameter L1, and a tip end angle is about 92 degrees. The center diameter L3 is set to ?2.5 mm, the seat diameter L2 is set to ?3.0 mm, and the shaft diameter L1 is set to ?3.25 mm. The ratio of the center diameter L3 and the seat diameter L2 is L3/L2=2.5 mm/3.0 mm=about 0.833, and the ratio of the seat diameter L2 and the shaft diameter L1 is L2/L1=3.0 mm/3.25 mm=about 0.92.

Abstract: In the DME fuel supply device for a diesel engine, the time necessary to retrieve DME fuel remaining in the injection system after stopping the diesel engine into the fuel tank can be reduced. In a non-injection state, a three-way valve (71) is controlled to be OFF to form a communication passage in the direction indicated by the arrow B and a two-way valve (72) is controlled to be ON. DME fuel delivered from a feed pump (5) is delivered to an aspirator (7), passed from an inlet (7a) to the outlet (7b) thereof and returned to a fuel tank (4). That is, the DME fuel circulates via the aspirator. A vapor-phase pressure delivery pipe switching solenoid valve (75) is controlled to be ON and opened so that flow can pass through a vapor-phase pressure delivery pipe (73) connecting the vapor-phase (4a) in the fuel tank (4) and the inlet of the fuel gallery (11).

Abstract: Since an aspirator 7 is disposed at a position lower than a fuel gallery 11 and an overflow fuel pipe 81, DME fuel remaining in the fuel gallery 11 and the overflow fuel pipe 81 can be more efficiently retrieved to a fuel tank 4 by a combined force of gravity and suction force produced in a suction port 7c of the aspirator 7. Since the vapor-phase pressure delivery pipe opening/closing solenoid valve 74 is disposed at a position higher than the fuel gallery 11, DME fuel in a liquid state remaining in the fuel gallery 11 and the overflow fuel pipe 81 is forcedly delivered under pressure to the suction port 7c of the aspirator 7 by a combined force of gravity and the pressure of a vapor phase 4b in the fuel tank 4. Accordingly, time taken to retrieve the DME fuel in an injection system to the fuel tank after the stop of a diesel engine.

Abstract: In an exhaust gas cleaning apparatus (30) in which a before and after differential pressure (?P) of a filter (32) used to trap particulates is detected for regeneration of the filter (32), a time at which, during filter regeneration, the temperature of the outlet section of the filter (32) falls below the temperature of the inlet section thereof (?T>M), using a first temperature sensor (36) and a second temperature sensor (37), is determined as being the timing of the completion of the regeneration of the filter (32). The value of the before and after differential pressure (?P) at the time of this regeneration completion is used to estimate the quantity of residual ash in the filter (32), and when this estimated residual ash quantity is the same as, or greater than, a prescribed value (PX), a replacement warning signal (K3) is output urging replacement of the filter (32).

Abstract: A bypass controller (30) controls ON/OFF of a three-way electromagnetic valve (62) according to a detection value of a cam chamber sensor (12a). When the cam chamber sensor (12a) detects a viscosity of lubricant exceeding a predetermined allowable value, the three-way electromagnetic valve (62) is controlled to turn ON so that the output side of an oil separator (13) communicates with a bypass route (61). The pressure in the cam chamber (12) is reduced to or below the atmospheric pressure by suction of a compressor (16) with a check valve (14) regulating the pressure in the cam chamber (12) to the atmospheric pressure or above in the bypassed state. When the detection value of the viscosity of the lubricant output by the cam chamber sensor (12a) has become the predetermined allowable value or below, the three-way electromagnetic valve (62) is controlled to turn OFF so that the output side of the oil separator (13) communicates with the check valve (14) and the bypass route (61) is cut off.

Abstract: In an electronic control unit 31, a duty conversion map 41 from which a driving duty in energizing and driving an electromagnetic coil, not shown, of an electromagnetic vacuum adjustment valve 12 on the basis of a variable equivalent to target quantity of feedback of exhaust gas, for example, the magnitude of a desired negative pressure to a negative pressure output port (not shown) of the electromagnetic vacuum adjustment valve 12, and a duty correction map 42 from which a correction value for the driving duty is acquired on the basis inputted battery voltage and engine cooling water temperature, are provided. The driving duty is multiplied by the correction value acquired from the duty correction map 42, and on the basis of the corrected driving duty, energization to the electromagnetic vacuum adjustment valve 12 is performed by a driving circuit 26.

Abstract: A fuel feed pump is provided that has a fuel flow-rate regulating valve, on the inlet side. The fuel flow-rate regulating valve includes a housing with a fuel inlet port and a fuel outlet port, a valve mechanism for controlling the flow rate of the fuel from the inlet port to the outlet port, and a regulating mechanism for regulating a backpressure to control the position of a needle valve of the valve mechanism in response to a system pressure, to thereby control the flow rate by controlling the fuel flow through an opening provided in a valve chamber. This arrangement makes it difficult for contamination to accumulate, and also enables a low-cost implementation.

Abstract: A ceramic material has piezoelectric characteristics, can be sintered at low temperature, and is suited to various piezoelectric devices. The ceramic material primarily includes Pb, Zr, and Ti and has the general formula ABOd, in which A is (Pb1?aM1a?b), where M1 is selected from the group consisting of group 3A elements, Li, Na, K, Mg, Ca, and Sr, and B is [(M21/3Nb2/3?c)?Zr?Ti?], where M2 is one or more elements capable of forming at least a perovskite structure in the ceramic material, or the formula PbxM31?x[(M41/3Nb2/3)e(Co1/3Nb2/3)f(Zn1/3Nb2/3)gZrhTii]O3, where M3 denotes one or more elements selected from among the group consisting of La, K, Er, and Yb and M4 denotes an element selected from among the group consisting of Ni, Mn, and Sr. The ceramic material can be prepared by sintering at a temperature of 950° C.

Abstract: In a negative pressure boosting device of the present invention, upon depression of a pedal at a normal speed, an input shaft 11 and a valve plunger 10 move forward to close a vacuum valve 15 and open an atmospheric valve 16 and a power piston 5, a valve body 4, and an output shaft 24 move forward. In the initial stage of operation, hooks 27c and 31a are not engaged with each other so that a cylindrical member 27 does not move forward, thereby shortening the stroke of the input shaft 11 as compared to a conventional one. Upon rapid depression of the pedal, a press face 10a presses a pressed face 27e so as to deform an engaging arm portion 27b, thereby disengaging the hooks 27c and 31a from each other. The cylindrical member 27 is moved backward by a spring 30 to push a vacuum valve portion 12b so that the atmospheric valve portion 12a is spaced apart from the atmospheric valve seat 14 more rapidly than that of the service braking, thereby increasing the jumping amount and thus rapidly intensifying the output.

Abstract: Unit-specific identification data (IDA, IDB) of a transmission electronic control unit (5) and an engine electronic control unit (4) are stored in memories (5A, 4A), and engine start data (DES) required for starting an engine (2) are stored in the memory (4A) of the transmission electronic control unit (5). At the time of engine starting, the validity of the combination of the transmission electronic control unit (5) and the engine electronic control unit (4) is checked in the transmission electronic control unit (5) based on the identification data (IDA, IDB), and the engine start data (DES) are sent from the transmission electronic control unit (5) to the engine electronic control unit (4) in response to a request from the engine electronic control unit (4) only when validity is confirmed.

Abstract: Since an aspirator 7 is disposed at a position lower than a fuel gallery 11 and an overflow fuel pipe 81, DME fuel remaining in the fuel gallery 11 and the overflow fuel pipe 81 can be more efficiently retrieved to a fuel tank 4 by a combined force of gravity and suction force produced in a suction port 7c of the aspirator 7. Since the vapor-phase pressure delivery pipe opening/closing solenoid valve 74 is disposed at a position higher than the fuel gallery 11, DME fuel in a liquid state remaining in the fuel gallery 11 and the overflow fuel pipe 81 is forcedly delivered under pressure to the suction port 7c of the aspirator 7 by a combined force of gravity and the pressure of a vapor phase 4b in the fuel tank 4. Accordingly, time taken to retrieve the DME fuel in an injection system to the fuel tank after the stop of a diesel engine.

Abstract: In a state in which a high-pressure control solenoid valve is driven to control the pressure in a common rail (refer to Step S100), when the pressure in the common rail exceeds a predetermined value (refer to Step S104), a driving current determined by a prescribed value map that defines the correlation between the pressure in the common rail and the driving current of the high-pressure control solenoid valve is corrected based on an actual pressure in the common rail and the driving current of the high-pressure control solenoid valve at the actual pressure (refer to Steps S106, 108, S110, 112), and the corrected driving current is passed to the high-pressure control solenoid valve, thereby ensuring appropriate and stable injection control even when there exists a variation in operational characteristics among pressure control valves.

Abstract: In an electronic control unit 31, a duty conversion map 41 from which a driving duty in energizing and driving an electromagnetic coil, not shown, of an electromagnetic vacuum adjustment valve 12 on the basis of a variable equivalent to target quantity of feedback of exhaust gas, for example, the magnitude of a desired negative pressure to a negative pressure output port (not shown) of the electromagnetic vacuum adjustment valve 12, and a duty correction map 42 from which a correction value for the driving duty is acquired on the basis inputted battery voltage and engine cooling water temperature, are provided. The driving duty is multiplied by the correction value acquired from the duty correction map 42, and on the basis of the corrected driving duty, energization to the electromagnetic vacuum adjustment valve 12 is performed by a driving circuit 26.

Abstract: An existing diesel engine vehicle of light oil fuel is enabled to run as a diesel engine vehicle using DME as fuel without exchanging a whole diesel engine and at very low cost and easily. The shape of a tip part 21 of a needle valve 2 is set by a center diameter L3 for regulating a minimum flow path area at full lift of a fuel injection nozzle 1, a seat diameter L2 of a seat part 211 coming in contact with a valve seat part 33 and blocking communication with a fuel injection hole 31, and a shaft diameter L1, and a tip end angle is about 92 degrees. The center diameter L3 is set to ?2.5 mm, the seat diameter L2 is set to ?3.0 mm, and the shaft diameter L1 is set to ?3.25 mm. The ratio of the center diameter L3 and the seat diameter L2 is L3/L2=2.5 mm/3.0 mm=about 0.833, and the ratio of the seat diameter L2 and the shaft diameter L1 is L2/L1=3.0 mm/3.25 mm=about 0.92.

Abstract: In an injection pump element 2, a communication route for communicating an injection pipe 3 connected to a fuel liquid outlet 212 and an inner peripheral surface of a plunger barrel 25 is formed by a purge passage 242 formed in a delivery valve seat 24, a purge passage 252 formed in the plunger barrel 25, and a purge port 253. When the injection pump element 2 is in a non-injection state, the plunger 26 is rotated circumferentially to such a rotational position that a purge groove 265 formed in an outer peripheral surface of the plunger 26 and a purge port 253 formed in an inner peripheral surface of the plunger barrel 25 are communicated to each other. The purge groove 265 is communicated to a fuel gallery 11 via a hole 263 and a notch 262. When the injection pump element 2 is in the non-injection state, the injection pipe 3 is communicated to the fuel gallery 11 even if the delivery valve 23 is closed.

Abstract: A sun gear 6 is concentrically, rotatably disposed inside an internal gear 4. Plural planet gears 8, carried by a planetary carrier 10, are disposed between and in meshing engagement with the internal gear 4 and the sun gear 6. The planetary carrier 10 is connected to a shaft extending from an engine while the internal gear 4 and the sun gear 6 are connected to output shafts. The internal gear 4 is molded by a plastic working, followed by a thermal treatment including soft-nitriding, a nitriding and a carburizing hardening step. The inner surface of the internal gear 4 is formed with internal gear teeth 4b, except for an axial portion 4d, while a spline groove 4a is formed on the outer surface of the internal gear 4 at a location corresponding to the portion 4d where no internal teeth 4b are formed for engagement with a spline 2a on a housing 2. The internal gear 4 is reduced in size while improving the mechanical strength thereof.

Abstract: In a state in which a high-pressure control solenoid valve is driven to control the pressure in a common rail (refer to Step S100), when the pressure in the common rail exceeds a predetermined value (refer to Step S104), a driving current determined by a prescribed value map that defines the correlation between the pressure in the common rail and the driving current of the high-pressure control solenoid valve is corrected based on an actual pressure in the common rail and the driving current of the high-pressure control solenoid valve at the actual pressure (refer to Steps S106, 108, S110, 112). The corrected driving current is passed to the high-pressure control solenoid valve, thereby ensuring appropriate and stable injection control even when there exists a variation in operational characteristics among pressure control valves.