Patent Application
20070006850
1. Field of the Invention
The present invention relates to a system for front connection between a tubular rail for high-pressure fluid, and to a system for reducing the size of the rail. In particular, the invention relates to a system that enables a reduction in the radial stresses to which the ends of the rail are subjected, for example in a system for supplying fuel for an internal-combustion engine.
2. Description of the Related Art
As is known, in internal-combustion engines with fuel injection, referred to as “common-rail engines”, the fuel is brought up to a high pressure, in the region of at least 1600 bar, by means of a high-pressure pump, which sends the fuel to a common rail, having in general a tubular shape, which is in communication with each individual injector. In addition, the rail must be connected to other elements, such as a delivery duct of the high-pressure pump, a pressure sensor, a pressure-limiting valve, etc.
In modern injection engines, the aim is to reduce more and more the size of the rail, whilst for reasons of costs the target is to simplify its fabrication. Tubular fluid rails are known, made from normal-production pipes that enable the rails to be obtained at a lower cost than the ones obtained by forging. Said rails moreover each have at least one terminal portion that must be connected to a coaxial element of the aforesaid type.
Fluid rails of the known art in general present the drawback of requiring brackets that perform the dual function of enabling gripping of the piece being produced and of enabling its fixing to the engine. In the case where the tubular body is made from a normal-production pipe, the brackets must then be welded, or in any case constrained by means of some other type of connection, to the tubular body with an evident increase in costs and complication in the fabrication process. In the case where the tubular body is obtained by forging, the brackets in any case entail an increase in the weight of the entire system.
One goal of the invention is to eliminate the brackets present in fluid rails of the known art, by means of appropriate solutions that afford high reliability and of limited cost.
According to the invention, the above goal is achieved by a system for reducing the dimensions of a rail for high-pressure fluid, set forth herein.
In particular, the above aim is achieved by providing a milling on the tubular body, which will not entail any oversizing thereof.
Another goal of the invention is to provide a system for connection of a tubular fluid rail to a coaxial element, without reducing its resistance to radial stresses.
According to the invention, the above further goal is achieved by a system for front connection between a tubular rail for fluid under pressure and at least one element coaxial thereto, as set forth herein.
In particular, the connection system is characterized in that both the usual pressure transducer and the usual connection for supply from the high-pressure pump are connected coaxially to the tubular rail, in a position corresponding to the ends thereof.
For a better understanding of the invention, a preferred embodiment is described hereinafter, purely by way of example, with the aid of the attached drawings, wherein:
With reference to
For this purpose, the tube 7 has a swollen end 11, whilst the device 9 comprises a sleeve 13 threaded on the outside, which is fixed on the hollow body 6 in any known way. Screwed on the sleeve 13 is a ring nut 14, which, via a bushing 16, is designed to block the end 11 of the tube 7 against the hollow body 6. In particular, in the two tubes 7 on the left in
The hollow body 6 has a pre-set internal diameter d (
Once the value of the internal diameter d has been defined so as to optimize the behaviour of the supply pressure during operation, the minimum admissible value of the external diameter Dmin is determined. In fact, this minimum value must be such as to bestow upon the hollow body 6 the sturdiness necessary for withstanding the stresses induced by the pressure within the hollow body 6 during normal operation of the engine. Hence, the external diameter D of the hollow body 6 must be assumed greater than or equal to Dmin taking into account that, the greater said diameter D, the greater the overall dimensions, weight and costs.
According to a purpose of the invention, to enable gripping of the hollow body 6 during production, or to carry out normal maintenance operations during engine life, in a position corresponding to each terminal portion 17 and 18 of the hollow body 6 two millings 31 and 32 are performed, which define two shoulders 33 and 34 on the outer surface of the hollow body 6. Designated by 27 and 28 are instead two shoulders internal to the hollow body 6, defined in a position corresponding to a variation of the internal diameter, which is brought from the value d to a value d′ greater than d, by means of two internal millings of the terminal portions 17 and 18.
Hereinafter, D′ designates the diameter of the largest circumference circumscribed in the cross section of the tubular body 6 in a position corresponding to the millings 31, 32, which can have a circular or else a prismatic cross section. In particular, each external milling 31, 32 can have a hexagonal cross section to enable blocking of the rail 5 using appropriate tools.
The internal milling of the terminal portions 17, 18 must be obtained in such a way that the shoulders 27 and 28 are set in a position corresponding to the portion of the hollow body 6 with external diameter D; i.e., they must belong to a cross section of the tubular body 6 with external diameter D. Consequently, each external milling 31, 32 must have a length smaller than the corresponding internal milling.
The external millings 31 and 32 locally reduce the radial strength of the hollow body 6. Since enclosed within the hollow body 6 is fuel at a high pressure, there would derive the need to oversize the diameter D, in such a way that the diameter D′ is still greater than or equal to the diameter Dmin defined previously.
The terminal portions 17 and 18 of the hollow body 6 are designed to be connected at the front to corresponding coaxial elements 19 and 21. In particular, the element 19 represents a union for connection of the hollow body 6 with a delivery pipe (not shown) of the high-pressure fuel pump. The element 21 represents a union for connection of a pressure transducer 20, for determining the pressure of the fuel in the rail 5.
Each of the two elements 19 and 21 has a corresponding cylindrical hollow portion 22 and 23, having an external diameter substantially equal to the internal diameter d′ of the corresponding terminal portion 17, 18 of the hollow body 6. Consequently, hereinafter d′ designates also the external diameter of each cylindrical portion 22, 23. This cylindrical portion 22, 23 moreover has an internal diameter d″ smaller than the internal diameter d of the hollow body 6.
The two coaxial elements 19 and 21 each have an external thread in a position corresponding to the respective cylindrical portion 22 and 23, which has a nominal diameter equal to the aforesaid external diameter d′. The external thread engages a similar internal thread of the hollow body 6. It is understood that the internal diameters d′ of the internal millings of the terminal portions 17 and 18 of the hollow body 6 can differ from one another.
Each cylindrical portion 22 and 23 terminates with a front surface 24 and 26, which is annular and plane. Set between each front surface 24 and 26 and the corresponding shoulder 27 and 28 is a corresponding washer 29 and 30, which is made of a relatively soft material as compared to that of the hollow body 6 and of the two coaxial elements 19 and 21. In particular, the hollow body 6 of the rail 5 and the cylindrical portions 22 and 23 of the coaxial elements 19 and 21 are made of steel, whilst the washers 29 and 30 are made of soft iron.
The washers 29 and 30, providing the seal between the unions 19 and 21 and the hollow body 6, are such that the stresses to which the terminal portions 17 and 18 of the hollow body 6 are subjected are only due to the threaded connection and not to the pressure of the fuel. In this way, the radial stresses are much more contained, and consequently the diameter D′ proves sufficient to guarantee resistance of the hollow body 6 to these stresses. Without this solution, i.e., if the milling were obtained in an area corresponding to a high-pressure portion of the hollow body 6, it would be necessary to use a hollow body 6 with a larger external diameter D.
As an alternative to a threaded connection between the coaxial elements 19 and 21 and the hollow body 6, the cylindrical portions 22 and 23 of the coaxial elements 19 and 21 can have an external diameter D′ slightly greater than the internal diameter of the corresponding terminal portion 17 and 18 of the hollow body 6. In this way, each cylindrical portion 22 and 23 can be fixed on the terminal portion 17 and 18 of the hollow body 6 by axial force forcing, or else by exploiting thermal expansion, by means of pre-heating of each terminal portion 17, 18.
As regards the radial strength of the coaxial elements 19 and 21, the respective internal diameter d″ of the cylindrical portions 22 and 23 must be sufficiently smaller than the external diameter d′ so as to obtain a pre-set thickness d′-d″. In this way, the structural strength of the cylindrical portions 22 and 23 is guaranteed. As already mentioned, the coaxial element 19 is formed by a diameter adapter for the usual pipe for connection to the high-pressure fuel pump. In turn, the coaxial element 21 is made of a single piece with the pressure transducer 20, which can be replaced by a valve for controlling the pressure of the fuel in the rail 5. In either case, the internal diameter d″ of the cylindrical portion 22, 23 of the coaxial element 19, 21 is very small.
In the variant of
From the foregoing description, the advantages of the invention as compared to connections of the known art are evident. In particular, provision of the millings 31, 32 on the hollow body 6 enables secure and effective gripping thereof, whilst positioning of the millings 31, 32 themselves in the way indicated renders unnecessary any oversizing the diameter D of the hollow body 6 itself to guarantee the necessary structural strength.
All of the above U.S. patents, U.S. patent application publications, U.S. patent applications, foreign patents, foreign patent applications and non-patent publications referred to in this specification and/or listed in the Application Data Sheet, are incorporated herein by reference, in their entirety.
From the foregoing it will be appreciated that, although specific embodiments of the invention have been described herein for purposes of illustration, various modifications and improvements may be made to the connection system described above, without departing from the spirit and scope of the invention. Accordingly, the invention is not limited except as by the appended claims. For example, the union 19 can be made of a single piece with the delivery pipe of the high-pressure pump. In addition, the pressure transducer 20 can be located in a centroidal position of the hollow body 6, and hence set in a radial position, rather than an axial position, for example for reasons of engine arrangement.
| Number | Date | Country | Kind |
|---|---|---|---|
| 05425485.9 | Jul 2005 | EP | regional |
