referring to fig1 , numeral 10 generally designates a reciprocating pump with suction and force plungers , capable of working at high pressures for injecting concrete mixtures in order to increase mechanical or moisture - proofing characteristics of soils . the pump 10 in this embodiment is a reciprocating pump with several cylinders side by side in line , in each of which there runs a respective single - action suction and force plunger 11 , only one of which is shown in the drawing . in particular , according to certain embodiments , the pump includes a system having three plungers , which define a so - called “ triplex pump ”. the plunger 11 connected , by a connection system 12 ( here represented as a collar joint , but as a variant it also may be made using a tie - rod or similar component ) to a rod 13 driven by a crankshaft ( not shown ), by a respective connecting rod ( not shown ). the body 14 of the pump may be integral with a block 15 in which there are formed pumping chambers 16 , one for each plunger . the plunger may penetrate into the pumping chamber through an aperture 17 . by using a system of valves , the pumping chamber 16 reduces its volume as a result of the entry of the plunger 11 resulting in an increase in the pressure of the primary fluid contained therein . when the required pressure is reached , the valve ( not represented ) opens an outlet and the pressurized fluid is injected into the pumping line until it reaches the drilling machine . the pump described herein is not to be considered limited by the types of fluid with which it operates . in the remainder of the description and the annexed claims , the term “ primary fluid ” or “ first fluid ” refers to a fluid which is to be pressurized by the pump and injected into a soil . in many applications , the primary fluid will be a mixture containing cement ( for example water and cement , or water , cement and bentonite ). the expression “ second fluid ” or “ secondary fluid ” refers to a fluid which is used principally for lubricating the plungers ( or the plunger ) of the pump , according to procedures known per se . in certain embodiments , the second fluid includes lubricating oil . an important advantage of pumps according to certain embodiments of the present invention results from the presence of a third operating fluid , which is used to control the surfaces affected by the sliding of the plunger ( s ). this third cooling fluid can be , for example , water or an aqueous mixture or solution , suitable for the purposes set forth herein . the plunger 11 is sealingly supported and guided , in its reciprocating motion in a direction here described as “ longitudinal ”, by a sealing and guiding device designated overall by reference number 20 . the sealing device 20 includes a cylindrical sleeve 21 locked by clamping ring 22 arranged coaxially within a flanged supporting bush 23 . the bush 23 may be removably fastened to the body 14 of the pump . a closed circuit for forced lubrication , for a second fluid , such as oil , is formed in the sealing device 20 . the lubrication circuit may include two radial ducts formed in the inner sleeve and in the bush , specifically an oil inlet duct 24 , an oil outlet duct 25 , and an axially extended annular chamber 26 formed in the inner cylindrical cavity 27 of the sleeve , at the interface with the plunger . the inlet and outlet ducts for the secondary fluid may be inverted . on the two opposite sides of the lubrication chamber 26 , two respective annular oil sealing gaskets 28 , 29 may be arranged , fixed to the cylindrical sleeve 21 and acting against the plunger 11 . the gasket 28 may be oriented with its principal sealing lip extending toward the “ wet ” side , while the sealing gasket 29 itself also may be oriented with its principal sealing lip towards the “ wet ” side . this orientation allows the seal from the lubrication chamber 26 not to be hermetic towards the “ wet ” side , thus allowing a slow and continuous controlled leakage of lubricating fluid which serves to moisten a sealing gasket 37 , described hereinafter , thus keeping it lubricated . two further o - ring gaskets 30 , 31 may be interposed between the sleeve 21 and the supporting bush 23 , with sealing functions against the secondary lubricating fluid . at the end of the sleeve 21 , on the “ wet ” side facing towards the pumping chamber for the primary fluid , there is fitted in the internal cylindrical cavity 27 a first sealing gasket 32 against the primary fluid ( or “ cement seal ”); at the opposite end , on the dry side near the clamping ring 22 , there may be fitted a conventional scraper ring 33 . a cooling circuit with a third fluid , such as water ( or other liquid ) is formed in the sealing device 20 , with radial intake duct 34 and outlet duct 35 formed through the outer bush and the inner sleeve 21 , and an annular chamber 36 formed in the internal cylindrical cavity 27 of the sleeve around the plunger 11 . the intake and outlet ducts may be inverted with respect to what is shown , without altering the functionality of the system . the annular chamber 36 is sealed toward the “ wet ” side by the first sealing gasket 32 sealing against cement , while on the opposite side , facing towards the clamping ring 22 , the chamber 36 is sealed against the plunger 11 by a second guiding and sealing gasket 37 sealing against the primary fluid , particularly against cement mixtures . the second sealing gasket 37 may be axially interposed between the first sealing gasket 32 sealing against the first fluid and the annular chamber 26 of the lubrication circuit . as shown in the illustrated example , the second cement sealing gasket 37 is located adjacent to the oil sealing gasket 29 . the sealing gaskets 28 , 29 , 32 , 37 and the scraper 33 may be seated in respective annular grooves formed in the internal cylindrical cavity 27 of sleeve 21 . the second sealing gasket 37 , in addition to sealing against the cooling water , also serves as a guide element for the plunger 11 , and therefore its shape and the material from which it is made are chosen appropriately to resist high specific pressures . in a variant ( not shown ), the second sealing gasket 37 also may incorporate the functions of the sealing gasket 29 which therefore could be omitted . in this case the sealing gasket 37 directly delimits the annular chamber 26 of the second lubrication fluid , and also would perform sealing functions against the secondary fluid on the “ wet ” side as well as sealing the primary fluid and guiding the plunger piston 11 . as it reciprocates , the plunger 11 can move between an axially retracted position ( to the left in fig1 ) and an axially extended position ( to the right ) in which it enters deeper into the pumping chamber 16 . in every position taken by the plunger 11 along its stroke , at least a part of its cylindrical outer surface is always seated within the inner cylindrical cavity 27 and faces both of the annular chambers 26 and 36 . in the embodiment shown , enlarged in fig2 , the sealing gasket 37 has an annular body 38 from which protrude internally several annular reliefs , in this example three in number , suitable for sliding against the plunger 11 . a sealing lip 39 , of a generally truncated - conical shape , may project obliquely toward the wet axial side of the pump and radially towards the plunger . two annular reliefs 40 , 41 , axially spaced apart from one another , may project in radially internal directions , and each may terminate with a respective radially internal cylindrical surface suitable for guiding and stabilizing the plunger 11 . the sealing lip 39 may be located closer to the pumping chamber 16 , while the annular reliefs 40 , 41 are farther from the pumping chamber . the compartments or cavities formed between the annular reliefs 40 , 41 and between the relief 41 and the lip 39 , and open towards the plunger 11 , allow lubricating fluid coming from the leakage of sealing gasket 29 to be appropriated . this occurs because of the compartment identified between the two contiguous reliefs on which the specific pressure , necessary for guiding , is very high , unlike that which is generated in the cavities which is very low and which will favor the accumulation of lubricating fluid . the accumulation of lubricant helps to increase the life of the sealing gasket 37 . the alternation between full and empty also enables dispersal of the heat due to the friction between the internal cylindrical surface of the reliefs 40 and 41 , the lip 39 and the outer surface of the plunger 11 . in alternative embodiments ( not shown ), there may be only one of the two reliefs 40 , 41 , or , in a further embodiment , there may be more than two reliefs . in the embodiment shown in fig2 in undeformed condition , the annular reliefs 40 , 41 have an axial section of trapezoidal shape . the annular reliefs 40 , 41 considerably reduce the radial loads and the friction on the first frontal sealing gasket 32 , which originally serves to seal against cement . the plain cylindrical side on reliefs 40 and 41 , rather than the normal apex which can be found on profiles with a triangular section , ensures that the plunger 11 is correctly guided . the cylindrical inner surface of reliefs 40 , 41 may contain furrows or grooves suitable for allowing the passage of secondary fluid for lubricating at least one of the said reliefs and the sealing lip 39 . the second sealing gasket 37 also may function to provide a seal against cement . the third cooling fluid ( water or other liquid ) which circulates in the chamber 36 also serves to lubricate the second sealing gasket 37 and to further cool the plunger , by direct washing . this fluid therefore has two functions : the principal function of cooling the seals , the plunger and the sleeve , and the secondary function of lubricating sealing gaskets 32 and 37 which would not be reached by the secondary lubricating fluid . in fact the inner side , toward the “ wet ” part of sealing gasket 37 and the whole of sealing gasket 32 , would not be in contact with the secondary lubricating fluid . for this purpose , as a third fluid , it is possible to use liquids enriched with additives to improve this second function , or oil ( in this case , to offset a disadvantage caused by the contamination of a valuable fluid , which provides a further extension of the life of the sealing components and the other parts in relative movement and subject to the presence of abrasive fluids ( such as cement mixtures ). any contamination of the third fluid by the cement indicates wear on the first , outermost sealing gasket 32 . at the point when the first sealing gasket 32 deteriorates and loses its sealing function , it allows cement to pass which is diluted by the flow of water . in this case , however , unlike previously existing pumps , it is possible to determine that the water contains a second component , because the outlet allows the fluid to free - fall or fall into an open container , or to pass into a transparent tube close to the operator &# 39 ; s station . while lubricating oil requires a closed and filtered circuit , the water can be directed and handled more freely because it does not represent an environmental pollutant . the second m sealing gasket 37 , in the event of damage to the first sealing gasket 32 ( which is in direct contact with the cement zone and is therefore the most subject to deterioration ), allows the pump to maintain its functionality because , as a secondary function , it acts as a cement seal . in this way the cement is prevented from ending up in the oil lubrication system , which allows it to be isolated and better protected . furthermore , by inserting an overload sensor ( not shown ) in the washing line , downstream of the plunger , it is possible to detect the presence of cement in the cooling circuit , indicating that the first , outermost sealing gasket 32 is in a worn condition . this sensor will send a signal to a data processing unit ( not shown ), which , on processing the information , will display an alarm to the operator , on a control panel in a command area such as a warning light , an acoustic alarm or , if there is a monitor , a pop - up alarm with or without an audio signal . the overload sensor may be of a pressure type ( any inclusion of cement mixture inside the duct for the third fluid will increase the pressure necessary for the contaminated fluid to circulate ). alternatively , optical sensors may be used , such as those which measure fluorescence in uv light . such sensors are able to detect the presence of oil in water . they can therefore warn of a problem with the sealing of the system of lubrication with the secondary fluid . when the concentration of oil , coming from the leakage from sealing gasket 29 , in the third fluid is too high , a problem may be indicated with sealing gasket 29 . the combination of this sensor with the others described above can indicate either damage to sealing gasket 32 for the primary fluid and / or damage to sealing gasket 29 for the secondary fluid . finally , it is possible to set up a suitable filter on the collection line for the third fluid , this filter , too , being provided with an overload sensor , which can provide a warning when the concentration of contaminant has reached a threshold level . it will be appreciated that a worn condition of the outer sealing gasket 32 is detectable from the presence of cement in the third cooling fluid ( or liquid ), and that the combination of the cooling circuit with the addition of the second sealing gasket 37 increases the life of the first outer sealing gasket 32 , as it is possible to circumscribe an isolated volume which can contain cooling fluid and lubricant . since the second sealing gasket 37 still protects the seal , the operator can decide whether to proceed immediately with replacement or to defer it , without risking damage to the plunger 11 , the sleeve 21 or the lubrication circuit , or risking contaminating the lubricating oil . the invention thus results in lower maintenance costs , prolongation of life for the components ( especially for the final sealing gasket sealing against cement , and for the sleeve of the sealing device ), and extended and predictable maintenance intervals . a single maintenance intervention for changing the lubricating oil and the gaskets is possible . the state of wear of the sealing gaskets sealing against cement can be monitored . the gaskets no longer must be replaced only at scheduled and preventive maintenance intervals but can always be replaced promptly as soon as they are found to be in a worn condition . if necessary , if the final cement sealing gasket is moderately worn , it is possible to continue working without risking the sleeve or contaminating the oil , thanks to the second cement sealing gasket . operators in the drilling field will appreciate that the second sealing gasket makes it possible to complete not only the execution of the jet column in progress , but for example to complete all the columns for the day or to reach a weekend or other scheduled break set aside for ordinary and for extraordinary maintenance on site . thus it is possible to schedule maintenance activities without delaying planned production . finally , it is possible to keep the life and the efficiency of the secondary fluid seal monitored . it should also be appreciated that the description above and the illustrated embodiments are exemplary of the present invention and should not to be taken in any way as a limitation of scope , applicability or arrangement of components of the invention . the drawings and description , however , will provide those skilled in the art with a convenient outline for the implementation of the invention , while it will remain understood that various changes may be made to the function and arrangement of the elements described in the exemplary embodiments , without departing from the scope of the invention . for example , the number of plungers may vary depending on particular needs , or the sealing gasket 32 also may have the same secondary function of guiding the piston and be conformed in the same manner as the sealing gasket 37 .