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EP2687723A1 - Compresseur à piston refroidi à l'eau - Google Patents

Compresseur à piston refroidi à l'eau Download PDF

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Publication number
EP2687723A1
EP2687723A1 EP12176645.5A EP12176645A EP2687723A1 EP 2687723 A1 EP2687723 A1 EP 2687723A1 EP 12176645 A EP12176645 A EP 12176645A EP 2687723 A1 EP2687723 A1 EP 2687723A1
Authority
EP
European Patent Office
Prior art keywords
cooling water
water
sealing element
valve
output
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.)
Withdrawn
Application number
EP12176645.5A
Other languages
German (de)
English (en)
Inventor
Roland Tittel
Claus-Peter Schulze
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
JP Sauer and Sohn Machinenbau GmbH
Original Assignee
JP Sauer and Sohn Machinenbau GmbH
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by JP Sauer and Sohn Machinenbau GmbH filed Critical JP Sauer and Sohn Machinenbau GmbH
Priority to EP12176645.5A priority Critical patent/EP2687723A1/fr
Publication of EP2687723A1 publication Critical patent/EP2687723A1/fr
Withdrawn legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
    • F04B27/04—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/06—Cooling; Heating; Prevention of freezing
    • F04B39/064—Cooling by a cooling jacket in the pump casing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/10—Adaptations or arrangements of distribution members
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/10—Adaptations or arrangements of distribution members
    • F04B39/1046—Combination of in- and outlet valve
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
    • F04B53/08—Cooling; Heating; Preventing freezing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
    • F04B53/10—Valves; Arrangement of valves
    • F04B53/1087—Valve seats

Definitions

  • the invention relates to a water-cooled piston compressor with the features specified in the preamble of claim 1.
  • Water-cooled reciprocating compressors for generating compressed air are used in particular on ships.
  • the compressors are usually connected to a central cooling water supply.
  • the compressors usually have thermostatic valves, which ensure that no or only a reduced flow of cooling water flows through the compressor when commissioning the compressor, so as to suspend cooling until reaching the desired operating temperature.
  • the thermostatic valve switches the cooling water flow until it reaches a certain setpoint temperature so that it is either bypassed by the compressor or guided through a reflux in a closed circuit in the compressor.
  • a cooling water pump is provided on the compressor. Also during operation of the compressor, ie after reaching the operating temperature, this pump promotes cooling water from the central cooling water supply through the compressor.
  • the water-cooled reciprocating compressor according to the invention has at least one cooling water flow path which passes through the compressor and the areas of the compressor to be cooled.
  • the first cooling water flow path is the flow path which causes the cooling in the compressor.
  • at least one cooling water pump is preferably arranged, which conveys the cooling water through the cooling water flow path.
  • This cooling water pump is preferably arranged on the input side of the compressor. On the output side of the compressor, this opens at least one cooling water flow path in a thermostatic valve. This serves to guide the flow of cooling water during commissioning of the compressor so that, until a desired operating temperature is reached, the cooling water is circulated through the compressor without replacement or cooling, ie not discharged to the outside.
  • the cooling water supply on ships for which the compressor according to the invention is preferably provided, generally takes place in such a way that seawater is supplied for cooling and returned to the outside.
  • a central cooling water supply which supplies various systems with cooling water, provided.
  • Such a central cooling water supply could also be provided as a circuit with a central heat exchanger for cooling the water.
  • the thermostatic valve has two outputs.
  • a first exit is provided with a return line leading to the inlet side of the first cooling water flow path. Then, when the first outlet of the thermostatic valve is opened, cooling water from a compressor disposed on the cooling water pump can be circulated through the compressor. The cooling water then flows from the thermostatic valve through the return line back to the inlet of the first cooling water flow path and then through the compressor again to the thermostatic valve. This condition is used when the compressor is started up in order to achieve a rapid heating of the compressor to the desired operating temperature.
  • the thermostatic valve has a second outlet which is connected to a cooling water outlet.
  • cooling water is guided after reaching the desired operating temperature and then out, for example, out of the boat or directed to an external heat exchanger, where it is cooled and then optionally again the compressor for cooling, in particular via a central cooling water supply is supplied.
  • the first and the second outlet of the thermostatic valve can be opened or closed alternately.
  • a movable valve body is provided, which is arranged so that when it closes the first output, it opens the second output and, when it closes the second output, opens the first output.
  • the valve body is moved depending on temperature, which is effected for example by expansion of an enclosed medium when heated in a known manner.
  • the thermostatic valve is designed such that between the valve body and a valve seat on which the valve body for closing the first output comes to rest, an elastic sealing element is arranged, so that the valve body is sealed when closing the first output via a first elastic sealing element against the first valve seat.
  • an improved tightness of the thermostatic valve is achieved, so that when the first output, which is connected to the return line, is sealed, this is sealed so that even with a negative pressure in a central cooling water supply, the cooling water pump of the compressor no cooling water through the return line and can undesirably circulate the first sealed outlet of the thermostatic valve. In this way, increased reliability of the reciprocating compressor is achieved even with insufficient cooling water supply.
  • the first elastic sealing element is fixedly arranged on the first valve seat.
  • the thermostatic valve is designed so that also at the second output between the valve body and an associated second valve seat, an elastic sealing element, namely, a second elastic sealing element is arranged.
  • an elastic sealing element namely, a second elastic sealing element is arranged.
  • the valve body is preferably sealed when closing the second output via the second elastic sealing element against the second valve seat.
  • the second elastic sealing element prevents cooling water between the valve body and the second valve seat from being forced outwards through the second outlet in the starting phase of the compressor at normal pressure or overpressure in the valve. This ensures that all the cooling water in the circuit is conveyed, so that the compressor can be brought as quickly as possible to a desired operating temperature.
  • the second elastic sealing element is preferably fixedly arranged on the second valve seat.
  • the second sealing element could also be attached to the valve body and move together with it.
  • the valve body is preferably made of metal in a known manner.
  • the valve seats are preferably formed of metal in the valve housing of the thermostatic valve.
  • the elastic sealing elements described above are arranged between valve seat and valve body.
  • the valve body is tubular and arranged with its first end face of the first elastic sealing element opposite one another such that the first end end comes to rest on the first elastic sealing element for closing the first outlet.
  • the first elastic sealing element is preferably fixedly arranged on a first valve seat.
  • the valve body seals via its end edge against the elastic sealing element on the first valve seat. To open the front end of the valve body comes from the first sealing element out of engagement.
  • the valve body is tubular and lies with its second axial end face of the second elastic sealing element so that the second end end comes to close the second output to the second elastic sealing element for conditioning.
  • the second sealing element is preferably fastened to a second valve seat.
  • the valve body is designed or movable so that preferably, when it is in sealing contact with its first end face on the first sealing element, is spaced with its second front end of the second sealing element. Conversely, if the second front end in sealing engagement with the second sealing element, the first end face preferably spaced from the first sealing element to open the first output.
  • the elastic sealing elements are preferably made of an elastomer, in particular of rubber.
  • the first sealing element is further preferably disc-shaped.
  • the second sealing element is preferably annular, so that a flow through the free space in the interior can enter into the thermostatic valve or the tubular valve body. From the opposite end face of the valve body, the flow then exits again when this front end is spaced from the first sealing element.
  • the valve body further preferably has a cylindrical, in particular circular cylindrical outer circumference and is axially movably guided in a sealing ring which bears against the outer circumference.
  • This sealing ring is preferably held or located in a housing section of the valve housing between the first and the second outlet. In this way, the first of the second output is separated by the system of the sealing ring on the outer circumference of the valve body.
  • the sealing ring is preferably at least on its inner circumference, which rests against the outer circumference of the valve body, made of a plastic with good sliding properties such.
  • B polytetrafluoroethylene.
  • a slight sliding of the sealing ring is achieved on the outer circumference of the valve body.
  • the sealing ring has an inner ring made of a plastic with good sliding properties such.
  • polytetrafluoroethylene and a surrounding outer circumference outer ring made of an elastomer.
  • the outer ring of an elastomer is preferably tight against a housing portion of the valve housing, preferably in an outer periphery of the valve body facing annular groove. Thus, the entire sealing ring is held in the housing section.
  • Fig. 1 schematically a four-stage reciprocating compressor 2 with the cooling water flow paths is shown.
  • a cooling water flow path 4 which passes through the four cylinders 6 and the intercoolers 8 of the four stages.
  • the cooling water flow in the flow direction S first passes through two coolers 8 of the fourth and first stage, then through the cylinder 6 of the first stage, then through the cylinder 6 of the third stage, then through the two intercoolers 8 of the second and third stage and then through the cylinders 6 of the second and fourth stages.
  • a cooling water pump 10 is arranged, which promotes the cooling water through the cooling water flow path 4. At the end of the cooling water flow path.
  • thermostatic valve 12 This opens into a thermostatic valve 12.
  • the thermostatic valve 12 is connected at its input 14 to the end of the cooling water flow path 4 and has two outputs 16, 18.
  • the first output 16 is connected to a return line 20. This leads to the input side of the cooling water flow path 4 upstream of the cooling water pump 10.
  • the piston compressor shown is connected to a central cooling water supply, for example, on a ship such as a submarine.
  • the illustrated cooling water circuit is connected on the input side to its cooling water inlet 22 with the corresponding cooling water supply.
  • the output 18 of the thermostatic valve 12 is connected to the cooling water outlet 24.
  • the cooling water flows back into a central cooling water circuit and from there, for example, to a central heat exchanger, where it is cooled and then fed back to the cooling water inlet 22, or is derived for example from the boat to the outside in the surrounding water.
  • the invention described in more detail solves the problem that if the amount of cooling water at the cooling water inlet 22 or a negative pressure in the central cooling water supply and thus the cooling water inlet 22 the risk that during operation, the pump 10 sucks in cooling water via the return line 20, although the output 16 of the thermostatic valve 12 is closed. Then it can lead to overheating of the compressor, since no sufficient amount of cooling water is sucked from the cooling water inlet 22.
  • the thermostatic valve 12, as indicated by Fig. 2 is described in more detail, designed in a special way.
  • the thermostatic valve 12 has a valve housing 26, in which three terminals, namely the input 14, the first output 16 and the second output 18 are formed.
  • valve body in the form of a valve cylinder 28 is arranged inside the housing 26, a valve body in the form of a valve cylinder 28 is arranged.
  • the valve cylinder 28 is tubular, ie formed of a circular cylindrical shape and guided in the direction of its longitudinal axis X in the interior of the valve housing 26 movable.
  • the valve cylinder 28 slides with its outer circumference in the interior of a sealing ring in the form of the seal set 30.
  • the seal set 30 is held in a groove 32 in the portion of the valve housing 26.
  • the seal set 30 is formed in two parts and has an inner ring 34 made of polytetrafluoroethylene and an outer ring 36 in the form of an O-ring of an elastomer such as rubber.
  • the inner ring 34 of polytetrafluoroethylene allows easy sliding of the valve cylinder 28 in the inner ring 34, wherein the inner ring 34 is held by the surrounding outer ring 36 and due to its elastic properties in close contact with the outer circumference of the valve cylinder 28.
  • the sealing ring 30 on the outer circumference of the valve cylinder 28 separates the outputs 16 and 18 from each other.
  • a first valve seat 38 is formed in the valve housing 26, on which the valve cylinder 28 can come into abutment with its first front end or axial end 40.
  • a first elastic sealing element 42 is attached at the first valve seat 38.
  • the first sealing element 42 is made of an elastomer material, in particular rubber, and has a disc-shaped form.
  • the first sealing element 42 thus lies, when the valve cylinder 28 presses against the first valve seat 38, between the valve seat 38 and the front end 40 of the valve cylinder 28 both the valve seat 38 and the valve cylinder 28 sealingly and thus seals the seat on the first valve seat 38 ,
  • the axially opposite second front end or axial end 44 of the valve cylinder 28 comes to close the second output 18 to a second valve seat 46 to the plant.
  • a sealing element in the form of an annular second sealing element 48 is arranged for better sealing on the valve seat 46.
  • the second sealing element 48 is formed as a flat ring of an elastomer, in particular rubber.
  • the interior of the ring releases the inlet for the flow, so that the cooling water from the inlet 14 into the interior of the valve cylinder 28 can occur and can flow axially through the valve cylinder 28 to the outlet 16 when the output 18, as in the Fig. 2 shown is closed.
  • the valve cylinder 28 is moved in the axial direction by an expansion element 50 against the spring 52. Ie. at rest, the spring 52 holds the valve cylinder 28 in the in Fig. 2
  • the cylindrical peripheral wall of the valve cylinder 28 closes the second outlet 18 at the same time.
  • the first end face 40 of the valve cylinder 28 is separated from the first sealing element 42 spaced at the first valve seat 38, so that the cooling water can flow through the gap between the front end 40 and the first sealing element 42 into the first output 16.
  • the valve cylinder 28 is pushed away from the second valve seat 46, so that the front end 40 comes into sealing contact with the first sealing element 42 of the first valve seat 38.
  • cooling water can flow through the then forming gap between the second front end 44 and the second sealing element 48 into the second outlet 18.
  • the cooling water is supplied from the cooling water pump 10 through the compressor. If a negative pressure now prevails at the cooling water inlet 22 or too little cooling water is available, the sealing of the first outlet 16 by the first sealing element 42 in the thermostatic valve 12 ensures that the cooling water pump 10 can not suck in cooling water via the return line 20, then instead, the cooling water pump 10 continues to draw in cooling water from the cooling water inlet 22. So even with little available cooling water cooling of the compressor is achieved.
  • the second sealing element 48 is, as in Fig. 2 shown, the second output 18 sealed. This ensures that in the starting phase of the compressor no cooling water exits through the second output 18 into the cooling water outlet 24. Thus, in the starting phase, the cooling water from the flow path 4 is completely conveyed into the return flow line 20, so that a closed cooling water circuit is created. In this way, an improved temperature management of the compressor is achieved. On the one hand, a quick and safe achievement of the operating temperature is ensured and on the other hand also a sufficient cooling with insufficient cooling water supply ensured.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Compressor (AREA)
EP12176645.5A 2012-07-17 2012-07-17 Compresseur à piston refroidi à l'eau Withdrawn EP2687723A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP12176645.5A EP2687723A1 (fr) 2012-07-17 2012-07-17 Compresseur à piston refroidi à l'eau

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP12176645.5A EP2687723A1 (fr) 2012-07-17 2012-07-17 Compresseur à piston refroidi à l'eau

Publications (1)

Publication Number Publication Date
EP2687723A1 true EP2687723A1 (fr) 2014-01-22

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ID=46582581

Family Applications (1)

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EP12176645.5A Withdrawn EP2687723A1 (fr) 2012-07-17 2012-07-17 Compresseur à piston refroidi à l'eau

Country Status (1)

Country Link
EP (1) EP2687723A1 (fr)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN105332786A (zh) * 2015-12-11 2016-02-17 重庆小康工业集团股份有限公司 发动机用节温器座
CN105351075A (zh) * 2015-12-11 2016-02-24 重庆小康工业集团股份有限公司 汽油机用节温器安装组件
CN105464782A (zh) * 2015-12-11 2016-04-06 重庆小康工业集团股份有限公司 汽油机调温器安装结构组件
CN105464781A (zh) * 2015-12-11 2016-04-06 重庆小康工业集团股份有限公司 汽油机节温器安装结构总成

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3489170A (en) * 1966-06-17 1970-01-13 Arthur L Leman Slush pump valve assembly
US3872835A (en) * 1972-09-15 1975-03-25 Herbert Deutschmann Cooling water circulation for a supercharged internal combustion piston engine
US5983927A (en) * 1995-04-07 1999-11-16 Valois S.A. Inlet valve assembly
WO2007045052A1 (fr) * 2005-10-21 2007-04-26 Atlas Copco Airpower, Naamloze Vennootschap Dispositif pour empecher la formation de condensat dans un gaz comprime et groupe compresseur equipe dudit dispositif
WO2011090528A1 (fr) * 2010-01-22 2011-07-28 Ingersoll-Rand Company Système compresseur comprenant un dispositif de commande de flux et de température

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3489170A (en) * 1966-06-17 1970-01-13 Arthur L Leman Slush pump valve assembly
US3872835A (en) * 1972-09-15 1975-03-25 Herbert Deutschmann Cooling water circulation for a supercharged internal combustion piston engine
US5983927A (en) * 1995-04-07 1999-11-16 Valois S.A. Inlet valve assembly
WO2007045052A1 (fr) * 2005-10-21 2007-04-26 Atlas Copco Airpower, Naamloze Vennootschap Dispositif pour empecher la formation de condensat dans un gaz comprime et groupe compresseur equipe dudit dispositif
WO2011090528A1 (fr) * 2010-01-22 2011-07-28 Ingersoll-Rand Company Système compresseur comprenant un dispositif de commande de flux et de température

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN105332786A (zh) * 2015-12-11 2016-02-17 重庆小康工业集团股份有限公司 发动机用节温器座
CN105351075A (zh) * 2015-12-11 2016-02-24 重庆小康工业集团股份有限公司 汽油机用节温器安装组件
CN105464782A (zh) * 2015-12-11 2016-04-06 重庆小康工业集团股份有限公司 汽油机调温器安装结构组件
CN105464781A (zh) * 2015-12-11 2016-04-06 重庆小康工业集团股份有限公司 汽油机节温器安装结构总成
CN105351075B (zh) * 2015-12-11 2018-11-16 重庆小康工业集团股份有限公司 汽油机用节温器安装组件

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