• 专利附录
  • 专利说明
  • 权利要求
  • 类似技术
  • 同族专利
  • 引用文献
  • 法律状态
  • 优先权
    • 专利摘要:
    The present invention relates to a valve device for maintaining a precondition pressure in a cooling system of a vehicle (1). The valve device (19) comprises entry air passage (25), compressed air is supplied to an interior space (1221) of the cooling system and a piston (23) slidably arranged between an open position and a closed position in which it blocks the compressed air passage (25). The piston (23) comprises a first piston area (ai) which is in contact with a medium in said interior space (12a) of the cooling system and a second piston area (ag) which is in contact with compressed air with a substantially constant pressure (pg). The first piston area (a1) and the second piston area (ag) are dimensioned so that the piston (23) is displaced towards the open position when the pressure (p1) in said internal space (1Za) in the cooling system is below a predetermined pressure (pg) and towards it closed position when the pressure (pr) in said internal space in the cooling system exceeds the predetermined pressure (pe). (Fig. 2)
    公开号:SE1450139A1
    申请号:SE1450139
    申请日:2014-02-10
    公开日:2015-08-11
    发明作者:Mats Ekman
    申请人:Scania Cv Ab；
    IPC主号:
    专利说明:

    2G 25 30 35 However, a cooling system is not completely tight but there is inevitably a small leakage of both air and coolant from the cooling system during operation of the internal combustion engine.
    The leakage lowers the pressure level in the cooling system during operation of the internal combustion engine. However, the leakage is usually so small that the pressure level is only lowered in a regenerable manner during normal operation of the vehicle. The pressure level in the system can also drop if the pressure relief valve is opened and released air in an extreme operating condition when the coolant has expanded. When the coolant cools down after an operating period, it regains its original volume. This creates a negative pressure in the cooling system that corresponds to the leakage in the cooling system during the operating period.
    The expansion tank includes a non-return valve that opens and eliminates the negative pressure in the cooling system as the coolant cools. The non-return valve thus adjusts in arrears for the leakage that has occurred during operation. Transport vehicles can, however, be driven essentially around the clock without intermediate periods during which the coolant cools down. As a result, the non-return valve cannot supply air which corrects for the leakage in the cooling system. Even if the leakage of air and coolant is small, the leakage during a long continuous operating period can lower the overpressure to such a low level that there is a risk of cavitation damage to the coolant pump.
    US 2011- / 0308484 discloses an arrangement adapted to maintain a predetermined pressure in a cooling system. The arrangement comprises a line with a one-way valve, a tap and a pressure regulator which connects an expansion tank in the cooling system to a charge air line. When the pressure regulator detects that the pressure in the expansion tank is too low, it is set in an open position so that compressed air is led from the charge air line to the expansion tank. As soon as the pressure regulator senses that the predetermined pressure has been reached in the expansion tank, it is set in a closed position so that the flow of charge air to the expansion tank ceases.
    SUMMARY OF THE INVENTION The object of the present invention is to provide a valve device with few components with which a predetermined pressure can be maintained in a cooling system in a simple and reliable manner.
    This object is achieved with the cooling system of the kind mentioned in the introduction, which is characterized by the features stated in the characterizing part of claim 1.
    Valve device comprises a movably arranged piston which is displaced to an open position as soon as the pressure in the cooling system drops below a predetermined value. When the piston 10 is in the open position, the valve device delivers compressed air to the cooling system. The supply of compressed air quickly raises the pressure in the cooling system to the predetermined value. When the pressure has reached the predetermined value, the piston is displaced to a closed position in which the supply of compressed air is interrupted. The forces which create the displacement movement of the piston are related to the pressure of the pressure liquor, the pressure in the cooling system and the size of the piston articles on which said pressure acts. With knowledge of the pressure of the compressed air and the predetermined pressure in the cooling system, said piston products can be dimensioned in relation to each other so that the piston then opens the pressure in the cooling system when a predetermined value and closes when the pressure in the cooling system exceeds this value. A valve device with a slidable piston can be given a simple construction with few components while at the same time having a reliable function.
    According to an embodiment of the invention, the piston comprises a third piston area which is in contact with air of ambient pressure. Such a piston may comprise a side which is provided with the first piston area which is in contact with the pressure in the cooling system. The piston comprises, on the other hand, the second piston area which is in contact with the compressed air and the third piston area which is in contact with air of ambient pressure. This remaining third piston area is the difference between the first piston area and the second piston area. Such a piston may comprise a first portion having a first diameter and a second portion having a second diameter smaller than the first diameter, the first portion comprising an end surface forming the first piston area, the second portion comprising an end surface forming the the third piston area and that the surface in the transition between the first portion and the second portion forms the second piston area. The piston thus obtains one. simple construction.
    According to an embodiment of the invention, the valve device comprises a first component which is adapted to define the position of the piston in the open position. The piston is thus affected by forces which seek to bring it to the closed position and directional forces which seek to bring it to the open position. When the forces striving to move the piston towards the open position are greater than the forces striving to move the piston to the closed position, the piston receives a movement from the closed position.
    The movement of the piston must, for natural reasons, be stopped in a suitable open position. Said first component may constitute a stop surface or the like which comes into contact with a surface of the piston and stops the piston when it has reached a suitable open position. Said first component advantageously has a first end which is connected to a stationary unit and a second end which is connected to the piston. Thus, the first component can stop the piston in the open position when the piston has obtained a position at a certain distance from the stationary component. Said first component advantageously has resilient properties. With such properties, the first component can brake the piston in a relatively smooth manner when it reaches the open position. The first component can also provide a positioning of the piston also in relation to the stationary unit. The first component can thus, for example, position the piston in a radial position within a hollow space in which the piston is slidably arranged.
    According to an embodiment of the invention, the valve device comprises a second component which constitutes an airtight wall between an area of the pressure passage and ambient air. Since the compressed air in the compressed air passage and the ambient air act on the different pistons on the same side of the piston, compressed air passage must be separated from the area of air by the ambient pressure. This can be done with an airtight wall element which is attached to the piston and a wall surface which defines the hollow space in which the piston is slidably arranged. Said first and second components may constitute one and the same component. In this case, the component thus constitutes both an airtight wall at the same time as it has resilient properties which stop the piston in a suitable open position.
    According to an embodiment of the invention, the compressed air passage comprises a part which has a transverse stretch in relation to the direction of movement of the piston and that the piston is adapted to block this part of the compressed air passage in the closed position. The piston may have a corresponding transverse portion which adjusts the width of this part of the compressed air passage depending on the position of the piston. Thus, in the closed position, the piston can block this part of the compressed air passage so that the air flow through the compressed air passage ceases. The transverse portion of the piston may constitute the second surface area. Thus, the second piston area obtains a dual function.
    The compressed air passage may comprise a sealing means which, together with said portion of the piston, blocks the compressed air passage in the closed position. By means of a sealing member, a completely tight abutment between said portion of the piston and the sealing member can be obtained so that the pressure liquor flow in the compressed air passage ceases completely when the piston is in the closed position.
    According to an embodiment of the invention, the compressed air passage is arranged radially outside the piston and radially inside a wall surface defining a hollow space in which the piston is slidably arranged. The compressed air passage may have two parts with an axial stretch outside the portions of the piston of different diameters and a part with a radial stretch connecting the two axial parts.
    According to an embodiment of the invention, the valve device is adapted to direct compressed air to an internal space in an expansion tank in the cooling system. Since an expansion tank already contains air in an upper area, it is convenient to supply the compressed air to this area of the expansion tank. The supplied compressed air raises the air pressure in the area above the coolant in the expansion tank. The air pressure thus acts with a pressure force on the coolant in the expansion tank so that it obtains a corresponding pressure. The pressure of the coolant in the expansion tank is transferred to the coolant in other parts of the cooling system. Alternatively, the air can be supplied to the static line or other suitable place in the cooling system.
    According to an embodiment of the invention, the valve device is adapted to receive compressed air from a compressed air source in the form of an accumulator tank which stores compressed air for an existing compressed air system in the vehicle. In heavy vehicles, there is usually always access to compressed air that can be used to advantage for this purpose. During operation of a vehicle, a predetermined relatively high air pressure is generally maintained in an accumulator tank by a compressor driven by the combustion engine. Such accumulator tanks are relatively tight so that compressed air can be stored with a relatively large overpressure for long periods of time even when the vehicle is not in operation. If the pressure in the accumulator tank is very high, compressed air line may comprise a throttling means with a fixed throttle which defines the pressure which the compressed air has in the compressed air passage.
    According to an embodiment of the invention, the cooling system comprises a pressure relief valve. When the cooling system is pressurized with cold coolant, an increase in pressure is provided in the cooling system as the coolant is heated up to its operating temperature. In cases where compressed air is added in a cold cooling system, the pressure in the cooling system can become too high when the coolant reaches the operating temperature. With the help of the pressure relief valve, air is released from the cooling system when the pressure exceeds a too high level.
    BRIEF DESCRIPTION OF THE DRAWINGS In the following, as an example, a preferred embodiment of the invention is described with reference to the accompanying drawings, in which: Fig. 1 shows a cooling system in a vehicle with a valve device according to the invention, Figs. 2 shows the valve device in a closed position and Pig. 3 shows the valve device in an open position.
    DETAILED DESCRIPTION OF A PREFERRED EMBODIMENT OF THE INVENTION FIG. 1 schernatically shows a vehicle 1. The vehicle 1 is advantageously a heavy vehicle.
    The combustion engine 2 may be a supercharged diesel engine. The internal combustion engine 2 is cooled by coolant circulating in a cooling system. A coolant pump 3 circulates the coolant in the cooling system and through the internal combustion engine 2. After the coolant has cooled the combustion engine 2, it is led to a line 4 which comprises a friend exchanger 4a for cooling a retarder. Alternatively, the coolant can be used as a working medium in the retarder. The coolant is led from the line 4 to a thermostat 5 in the cooling system. Before the coolant reaches a normal operating temperature, the thermostat 5 is adapted to conduct the coolant, via a line 6, to the coolant pump 3 which is arranged in a line 7.
    When the thermostat S conducts the coolant to the coolant pump 3, the coolant can circulate in the cooling system without being cooled. As soon as the coolant reaches a temperature exceeding a feed-determined operating temperature, the thermostat 5 directs the coolant, via a line 8, to an air-cooled coolant cooler 9, which is mounted at a front part of the vehicle 1. The coolant is cooled by a cooling air stream in the coolant cooler 9. The cooling air flow is provided by a radiator 10 and by the vehicle's wind speed. After cooling in the coolant cooler 9, the coolant is led, via a line 11, back to the coolant pump 3 in the line 7.
    The volume of the coolant in the cooling system varies with the temperature of the coolant. The cooling system comprises an expansion tank 12 with an internal drain which absorbs the varying volume of the coolant. The expansion tank 12 in this case, via a line 13, is connected to the line 7 which is arranged on the suction side of the coolant purge 3. The expansion tank 12 comprises, at an upper portion, a removable lid 14 to enable the filling of coolant to the cooling system. The lid 14 comprises a diagrammatically shown overpressure valve 15. The overpressure valve 15 opens when the pressure in the expansion tank 12 exceeds a maximum acceptable pressure in the cooling system. The overpressure valve 15 can, for example, open at an overpressure of 0.9 bar. The expansion rod 12 also includes a check valve 16.
    The non-return valve 16 ensures that the pressure in the expansion tank 12 returns to the pressure of the ambient air. It thus opens and lets in air if a negative pressure arises in the expansion tank 12 in relation to the surroundings.
    The vehicle I is in this case provided with a source of compressed air in the form of an accumulator tank 17. The accumulator tank 17 contains compressed air which is used in a compressed air system to activate various components in the vehicle. During operation of the combustion engine 2, a compressor maintains a predetermined relatively high air pressure in the accumulator tank 17. Since an accumulator tank 17 has a very tight construction, the air pressure in the accumulator tank can be maintained relatively constantly for a long time after the vehicle's combustion engine '2 is closed. 1 and with it the compressed air driven components can be used as soon as the vehicle 1 is to be used. The accumulator tank 17 is connected to the expansion tank 12 via a compressed air line 18. Compressed air line 18 comprises a valve device 19 which is adjustable in a closed position in which it prevents compressed air from the accumulator tank 17 to the expansion tank 12 and in an open position which allows compressed air to be led from the accumulator tank. 17 to the expansion tank 12.
    Compressed air line 18 comprises a throttling means 20 which provides a fixed throttling of the compressed air which is led from the accumulator tank 17 to the expansion tank 12. The air reaching the valve device 19 thus has a lower pressure than the air in the accumulator tank 17. The presence of the throttling means 20 results in too high. This ensures that the expansion tank 12 is filled with air at a reasonable rate when the valve device 19 is in the open position. The fact that the air flow to the expansion tank is not too high is also important from a safety point of view if the lid 14 were to be opened by mistake. and To restrict the air, the restrictor 20 comprises a flow channel having a small cross-sectional area. With knowledge of the pressure in the accumulator tank 17, the throttling means 20 can be dimensioned so that the compressed air which is led to the valve device 19 and the expansion tank 12 has a suitable value.
    Compressed air line 18 also comprises a valve 21 with which the compressed air bypass between the accumulator tank 17 and the valve device 19 can be broken. A control unit 22 is adapted to open the valve 21 when the internal combustion engine 2 is started and to close the valve 21 when the internal combustion engine is switched off. Thus, the valve device 19 is not loaded with compressed air as the vehicle 1 is not in operation.
    Fig. 2 shows the valve device 19 in more detail. The valve device 19 comprises a valve body in the form of a piston 23 which is movably arranged in an axial direction in a hollow space extending through the walls of the expansion tank 12. The hollow space is defined by a wall surface 24. The piston 23 comprises a first portion 23a having a first diameter d; and a second portion 23b having a second diameter d; which is smaller than the first diameter di. The hollow space 24 is defined by a first wall surface 24a enclosing the first portion 23a of the piston. The first wall surface 24a forms a hollow space having a slightly larger diameter than the first portion 23a of the piston. The hollow unit space 24 is defined by a second wall surface 24b which has a radial inward extension relative to it. first wall surface 24a. The hollow space 24 is defined by a third wall surface 24c enclosing the second portion 23b of the piston. The third wall surface 240 forms a heel-shaped space with a slightly larger diameter than the second portion 23b of the piston.
    The valve arrangement comprises a compressed air passage 25 which is arranged in the gap-shaped space between the piston 23 and the wall surface 24 which defines the hollow space. The compressed air passage 25 comprises a first part 25a having an axial extension in a position radially outside the first portion 23a of the piston. The first part of the compressed air passage 25a has an outlet opening 25211 which discharges compressed air into the inner space 12a of the expansion tank. The first portion 23a of the piston has an end surface which constitutes a first piston area a; which is in contact with air in the internal space l2a of the expansion tank.
    The pressure liquor passage 25 comprises a second part 25b falling asleep a radial stretch adjacent to the second wall surface 24b. The piston 23 comprises a second piston area az which is in contact with compressed air in the second part 25b of the compressed air passage 25. The second part 25b of the compressed air passage 25 comprises a sealing member 26 which is attached to the second wall surface 2419. The sealing member 26 is adapted to come into contact with the second piston area a: when the piston 23 has been displaced to a closed position. In the closed position, the piston 23 can eliminate the flow of air through the compressed air passage 25. Fig. 2 shows the piston 23 in the closed position. The compressed air passage 25 comprises a third part 25c where it receives compressed air from the compressed air line IS via an inlet opening 2501. The third part 25c of the compressed air line has an axial extension in a position radially outside the second portion 23b of the piston. The second portion 23b of the piston includes an end surface which forms a third piston area a; which is in contact with air by ambient pressure 28.
    The piston 23 is connected at a peripheral portion, in connection with the third piston area, to a component 27. Component 27 has a circular cross-sectional liner and a distance between a first end and a second end. The component 27 is connected to the movably arranged piston 23 at a first end and to the third wall surface 24a at a second end. The component 27 thus forms a connection between the movably arranged piston 23 and the stationary wall surface 24. The component 27 also has resilient properties so that it slows the movement of the piston 23 with a spring force FS when it is moved from the closed position. The component 27 is dimensioned so that it stops the piston 23 in a predetermined open position. Component 27 also forms an airtight wall between the compressed air passage 25 containing compressed air and ambient air 28 with atmospheric pressure.
    The piston is actuated by a first force F; which is determined by the first piston area a] times the pressure pi prevailing inside the expansion tank 12. This first force Fi and the spring force FS of the component 27 strive to displace the piston 23 towards the closed position. The piston 23 is also actuated by a second force F; determined by the second piston area a; times the pressure pg of the compressed air and a third force F 3 determined by the third piston area a; times the ambient pressure p3. The second force P2 and the third force F; strives to displace the piston 23 towards the open position. Compressed air pressure p: and ambient pressure p; are substantially constant and thus the forces Fg, F; which strives to bring the piston to the open position. The spring force FS of the component 27 is also known. However, the pressure inside the expansion tank 12 and subsequently the pressure in the cooling system can vary during operation and thus the first force Fi which strives to bring the piston 23 to the closed position.
    According to the invention, the first piston area is a; and the second piston area a; dimensioned relative to each other so that the piston 23 is displaced towards the open position when the pressure pi in the space inside the expansion tank 12a drops below a predetermined pressure po and towards the closed position when the pressure pi in the space inside the expansion tank 12a exceeds the predetermined pressure po. The predetermined pressure pg is a pressure suitable to be maintained in the expansion tank 12 and in the cooling system.
    As soon as the pressure p; in the cooling system falls below the predetermined value pg, the first force F 1 which strives to bring the piston to the closed position is reduced. When the first force Fi is reduced to a value so that it together with the spring force Fs becomes less than the constant forces F; and Fg results in the piston 23 being displaced to the open position. Compressed air with the pressure pz thus flows through the compressed air passage 25 and into the expansion tank 12. The pressure p; thus rises in the expansion tank 12. The increasing pressure pi in the expansion tank 12 acts on the first area a of the piston; which leads to the first force F; increases. When the sum of the first force P1 and the capercaillie force Fs becomes larger than the constant forces Fa and P3, it results in the piston 23 being displaced to the closed position. The supply of compressed air to the expansion tank 12 ceases.
    The valve device 19 does not require any active control. As soon as there is a supply of compressed air in the compressed air passage 25, it maintains the predetermined pressure in the cooling system. By means of the valve device 19, a predetermined pressure can be maintained in the cooling system under essentially all operating conditions of the vehicle. In connection with the ignition in a vehicle being activated, the control unit 22 can open the valve 21 so that the valve device 19 provides access to compressed air in the compressed air passage. 25.
    Thus, compressed air can be led into the expansion tank 12 and pressurize the cooling system as soon as the coolant purge 3 starts. As a result, the requirement to arrange the expansion tank 12 at a suitable height above the coolant purge is reduced to prevent cavitation. As the temperature of the coolant rises after a cold start, the pressure in the cooling system increases. However, the pressure relief valve 15 prevents the pressure from rising too high.
    The invention is in no way limited to the embodiment described in the drawing but can be varied freely within the scope of the claims.
    权利要求:
    Claims (14)
    [1]
    1. l. Valve device for maintaining a predetermined pressure in a cooling system. in a vehicle (1), characterized in that the valve device (19) comprises a compressed air passage (25) which comprises an inlet (25c1) via which compressed air with a substantially constant pressure (pg) is absorbed and an outlet (25a1) via which compressed air is delivered to an interior space (1Za) of the cooling system and a piston (23) slidably arranged between an open position in which compressed air is led through the compressed air passage (25) to the interior space (12a) of the cooling system and a closed position in which it blocks air through the compressed air passage (25) to the interior space (12a) of the iryl system, the piston (23) comprising a first side with a first piston area (a1) which is in contact with a medium in said interior space (12a) of the cooling system, and a second side with a second piston area (ag) which is in contact with the compressed air with the substantially constant pressure (pz), the first piston area (ai) and the second piston area (az) being directed so that the piston (23) is displaced towards theopen position when the pressure (p1) in said internal space (l2a) in the cooling system is less than a predetermined pressure (pg) and towards the closed position when the pressure (p1) in said internal space (l2a) in the cooling system exceeds the predetermined pressure (pa).
    [2]
    Valve device according to claim 1, characterized in that the piston (23) comprises a third piston area (ag) which is in contact with air of the ambient pressure (pg).
    [3]
    Valve device according to claim 2, characterized in that the piston (23) comprises a first portion (23a) having a first diameter (di) and a second portion (2311) having a second diameter (de) smaller than the first diameter ( di), wherein the first portion comprises an end surface forming the first piston area (a1), the second portion comprises an end surface forming the third piston area (ag) and the surface in the transition between the first portion (23a) and the second portion ( 23b) forms the second .colar area (ag).
    [4]
    Valve device according to one of the preceding claims, characterized in that the valve device (i 9) comprises a first component (27) which is adapted to define the position of the piston (23) in the open position.
    [5]
    Valve device according to claim 4, characterized in that said first component (27) has a first end connected to a stationary unit and a second end connected to the piston (23). '10 15 20 25 30 35 12
    [6]
    Valve device according to claim 5, characterized in that said first component (27) has resilient properties.
    [7]
    Valve device according to one of the preceding claims, characterized in that the valve device (19) comprises a second component (27) which constitutes an airtight wall between an area of the compressed air passage (25) and ambient air (28).
    [8]
    Valve device according to claims 6 and 7, characterized in that said first component and said second component element constitute the same component (27).
    [9]
    Valve device according to one of the preceding claims, characterized in that the compressed air passage (25) has a part (25b) with a transverse extension relative to the direction of movement of the piston (23) and that the piston (23) is adapted to block this part (25b ) of the compressed air passage (25) in the closed position.
    [10]
    Valve device according to claim 9, characterized in that the piston (23) is adapted to block the compressed air passage with a portion comprising the second piston area (ag).
    [11]
    Valve device according to one of the preceding claims, characterized in that the compressed air passage (25) comprises a sealing member (26) which, together with the piston (23), blocks the compressed air passage (25) in the closed position.
    [12]
    Valve device according to one of the preceding claims, characterized in that the compressed air passage (25) is arranged radially outside the piston (23) and radially inside a wall surface (24) which defines a hollow space in which the piston (23) is displaceably arranged.
    [13]
    Valve device according to one of the preceding claims, characterized in that the valve device (19) is adapted to conduct compressed air to an internal space (12a) in an expansion tank (12) in the cooling system.
    [14]
    14. l4. Valve device according to one of the preceding claims, characterized in that the valve device (19) is adapted to receive compressed air from a compressed air source in the form of an accumulator tank (17) which stores compressed air for an existing compressed air system in the vehicle (1).
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    同族专利:
    公开号 | 公开日
    SE538660C2|2016-10-11|
    DE112015000401T5|2016-11-03|
    DE112015000401B4|2020-12-24|
    WO2015119567A1|2015-08-13|
    引用文献:
    公开号 | 申请日 | 公开日 | 申请人 | 专利标题
    CH373225A|1959-12-17|1963-11-15|Gratzmuller Jean Louis|Process for cooling an engine unit comprising at least one internal combustion engine and installation for implementing this process|
    FR2529951B1|1982-07-08|1984-12-14|Renault Vehicules Ind|
    US7152555B2|2001-02-20|2006-12-26|Volvo Trucks North America, Inc.|Engine cooling system|
    DE102007058575B4|2007-12-05|2013-08-01|Man Truck & Bus Ag|Motor vehicle with compressed air based cooling system|
    DE102009018012B4|2009-04-18|2021-02-04|Daimler Ag|Method for controlling the system pressure in a coolant circuit|
    US20110308484A1|2010-06-16|2011-12-22|Russell Peterson|Method and apparatus to regulate coolant pump inlet pressure|
    SE535942C2|2011-02-25|2013-02-26|Scania Cv Ab|Cooling system in a vehicle|
    KR20130065135A|2011-12-09|2013-06-19|현대자동차주식회사|Pressure cap for surge tank at cooling system in vehicle|
    法律状态:
    优先权:
    申请号 | 申请日 | 专利标题
    SE1450139A|SE538660C2|2014-02-10|2014-02-10|Valve device for maintaining a predetermined pressure in a cooling system of a vehicle|SE1450139A| SE538660C2|2014-02-10|2014-02-10|Valve device for maintaining a predetermined pressure in a cooling system of a vehicle|
    DE112015000401.7T| DE112015000401B4|2014-02-10|2015-02-09|Valve arrangement for maintaining a predetermined pressure in a cooling system|
    PCT/SE2015/050138| WO2015119567A1|2014-02-10|2015-02-09|Valve arrangement to maintain a pre-determined pressure in a cooling system in a vehicle|
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