• 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 invention relates to a cylinder head (1) for a two - stage reciprocating compressor, comprising an intercooler (9) designed as a cooled overflow channel (14) between the first stage pressure side (8) and second stage suction side (10), the overflow channel (14) having an inlet Having substantially slit-like cross-section and additionally by at least one indirectly cooled central rib (15) is divided so that therefrom at least two Überströmkanalteile (14 ') and (14 ") arise whose cross-section in one dimension is substantially smaller than transverse to the indirectly cooled midrib ( 15) has a foot width of less than one third of the foot width of a conventional, water-cooled rib, corresponds in terms of heat dissipated, no disadvantages and in terms of production and operation of the skilled artisan readily apparent advantages.
    公开号:AT512923A4
    申请号:T50056/2013
    申请日:2013-01-25
    公开日:2013-12-15
    发明作者:Roland Dipl Ing Cesak；Bernhard Dr Spiegl；Andreas Dipl Ing Brandl
    申请人:Hoerbiger Kompressortech Hold；
    IPC主号:
    专利说明:

    Cylinder head for two-stage reciprocating compressor
    The invention relates to a cylinder head for a two-stage reciprocating compressor, with a designed as a cooled overflow between the pressure side of the first stage and suction side of the second stage intercooler, wherein the overflow channel has a Chen wesenti-5 slot-like cross-section.
    Nowadays, commercial vehicles, such as trucks, buses, construction machinery or rail vehicles, mostly supported by compressed air brakes on the supply of compressed air usually provided by the serving as a drive of the vehicle engine compressor is provided, which often also more Teilys-10 th of Vehicle, such as the air suspension supplied. The suction and pressure valves together with the associated inlet and Ableitkanälen having cylinder head of this compressor is nowadays usually integrated into the cooling circuit of the engine, so even at long time at high speed running compressor or longer time required high compression power, the temperature level of the compressor according to the 15th can be kept low. Temperature problems thus occur mainly in the pressurized gas, which should not be cooled as lossless as possible at the output of the reciprocating compressor before entering the second compressor stage in two-stage reciprocating compressor, so that the maximum temperatures occurring of the gas do not exceed a certain degree. Furthermore, a lower inlet temperature of the gas relative to the second compressor stage results in an increase in the capacity of the reciprocating compressor.
    The sucked ambient air is usually passed through the suction pipe of the first stage in the suction chamber. After a working stroke of the piston of the first stage, it passes as a pressurized gas via the pressure valve in the pressure chamber of the first stage. About a cooled than 25 overflow between the pressure side of the first stage and suction side of the second stage formed intermediate cooler, the compressed gas is passed into the suction chamber of the second stage, further compressed and leaves, after this two-time compression, the reciprocating compressor. Such intercoolers are known in various versions for a long time, although mostly worked with separately cooled wall elements or the like 30.
    From DE 10 2005 012 202 A1 a cylinder head of the type mentioned is known in which the pressure chamber of the first stage and the suction chamber of the second stage to a -1-
    826 AT
    Intermediate chamber are combined with water-cooled webs. In the preferred embodiment, these water-cooled webs are designed as castings. Another embodiment provides for the use of a sheet metal part forming the water-cooled webs. Both variants provide that each of the webs is designed water-cooled. Since the cooling water-carrying cross-section of the webs to avoid stall and increased friction in the cooling water, can not be arbitrarily reduced, the compressed air to be cooled is due to the limited space in the cylinder head, only a very limited volume available. For this reason, therefore, the heat transfer from the compressed gas into the cylinder head cooling in the known design can not be further optimized.
    Object of the present invention is to provide a cylinder head of the type mentioned in such a way that the mentioned disadvantages of the known embodiment are avoided and that in particular the cooling effect on the compressed gas between the two stages, while maintaining a simple production possibility, can be improved. This object is achieved according to the present invention in that the overflow channel is additionally divided by at least one indirectly cooled central rib so that at least two Überströmkanalteile arise from it. The indirectly cooled center rib has a foot width equal to less than one-third of the foot width of a conventional water-cooled rib, with respect to the dissipated heat, no disadvantages and with respect to the production and operation (no additional supply of cooling medium necessary) for the skilled artisan readily recognizable advantages over the prior art. This allows the simple optimization of the cross-sectional ratios, without additional space and manufacturing costs, for example, for the finished further cooling medium leading channels, with a drastic increase in the surface at the heat-25 transition can take place to cool the compressed gas.
    Furthermore, it is provided in an advantageous embodiment of the invention that the cross section of the indirectly cooled central rib is divided in its longitudinal extent to form a passage gap between the two-way Überströmkanalteilen. This leads to a further increase in the surface of the heat exchange instead -30, to save a contact surface / Dichtfiäche and thus reduce manufacturing costs and associated costs. -2-
    826 AT
    A development of the invention provides that in the cylinder head several overflow channels are present which are each shared by at least one uncooled center rib which further improves the heat dissipation. It can further vary both the foot width of the center rib, as well as the width of the resulting slot-like channels in the longitudinal direction. A further embodiment of the invention consists in that the center rib has an at least approximately, rectangular or trapezoidal cross-section. This enables the production of the center rib by means of a multiplicity of different production methods which include both cutting and non-cutting methods.
    According to another embodiment of the invention, the overflow passages 10 extend from the first stage pressure chamber to the second stage suction chamber, the sum of the volumes of the first stage pressure chamber, intercooler and second stage suction chamber being greater than the volume of the ejected during a compression cycle first stage. This has the consequence that the gas remains for a longer time in the intercooler and thus emits as much of the heat generated in the course of compression. The subject invention is explained in more detail below with reference to Figures 1 to 5, which show by way of example, schematically and not limitation, an advantageous embodiment of the invention. 1 shows the upper and lower parts of the cylinder head in perspective view from above (ie in the direction of the cylinders of the reciprocating compressor not shown below) and FIG. 2 shows a horizontal section through the lower part of the cylinder head along the line II-II. FIG. 4 shows a sectional view along the line IV-IV in FIG. 3 and FIG. 5 shows the detail V in FIG. 4.
    The illustrated cylinder head 1 consists essentially of a cylinder head upper part 2 and a cylinder head lower part 3. In the cylinder head upper part 2 are a Ansaugöff-25 tion 4 and a pressure port 18. About the intake 4, the gas to be compressed, due to the downward movement of a piston, not shown Reciprocating compressor, sucked via the suction chamber 5 in the cylinder of the first stage, wherein the mammal valve not shown under the Saugventilöffnungen 6 is opened.
    As a result of the upward movement of said piston, the mammalian valve is closed and the pressurized gas passes via the opened pressure valve and its pressure-valve openings 7 into the pressure chamber 8 of the first stage. -3-
    Due to the upward movement of the first piston, the associated expulsion and the simultaneous downward movement of the second piston and the associated suction, the pressurized gas through the intercooler 9 in the suction chamber 10 of the second stage and the open mammal valve and its Saugventilöffhungen 11 in the second 5 cylinders of the reciprocating compressor promoted.
    In the course of the upward movement of the second piston of the reciprocating compressor, the second-stage mammalian valve is closed, the second-stage pressure valve is opened, and the compressed gas is expelled via the pressure-valve openings 16 into the second-stage pressure chamber 17. The twice compressed compressed gas leaves the reciprocating compressor over 10 the pressure port 18 in the cylinder head upper part. 2
    As can be seen in FIG. 4 and FIG. 5, the intercooler 9 consists of water channels 12 directly cooled ribs 13 which form the overflow channel 14, which is additionally divided by an indirectly cooled central rib 15 so that at least two overflow channel parts 14 'and 14 " arise whose cross-section in one dimension is substantially smaller than transverse 15 thereto wherein also a plurality of overflow 14 may be present, which are each shared by at least one uncooled central rib 15.
    The water channels 12, the directly cooled ribs 13 and the indirectly cooled central rib 15 are formed both in the cylinder head upper part 2 and in the cylinder head lower part 3. Apart from that, one of the two cylinder head parts 2 or 3 could also be combined with a smooth lid in which no channels are formed.
    It can also be seen in Fig. 5 as well as in Fig. 4 that the cross section of the indirectly cooled central rib 15 in its longitudinal extent to form a passage gap between the two-way Überströmkanalteilen 14 'and 14 " divided, which leads to the already mentioned advantages. It should be noted that the indirectly cooled central rib 15 can have a trapezoidal cross-section in addition to 25, as shown in FIGS. 4 and 5, at least approximately rectangular.
    The mounting holes 19-19 " " shown in Figs. 1, 2, and 3 are " and 20-20 "" are provided for the fixation of the cylinder head 1 on a cylinder to be presented underneath the piston compressor not shown.
    826 AT
    Apart from the specific design for a two-stage reciprocating compressor, such an executed intercooler could of course also be used for three-stage or multi-stage reciprocating compressors. 826 AT 5 -5-
    权利要求:
    Claims (6)
    [1]






    1. Cylinder head (1) for a two-stage reciprocating compressor, designed as a cooled overflow channel (14) between the pressure side of the first stage and suction side of the second stage intermediate cooler (9), wherein the overflow channel (14) has a substantially 5 slot-like cross-section thereby characterized in that the overflow channel (14) is additionally divided by at least one indirectly cooled central rib (15) so that at least two overflow channel parts (14) and (14 ") are formed therefrom.
    [2]
    2. Cylinder head (1) according to claim 1, characterized in that the cross section of the indirectly cooled central rib (15) is divided in its longitudinal extent to form a passage gap between the two-way Überströmkanalteilen (14 ') and (14 ").
    [3]
    3. Cylinder head (1) according to claim 1 or 2, characterized in that a plurality of overflow channels (14) are present which are each shared by at least one indirectly cooled central rib (15).
    [4]
    4. Cylinder head (1) according to one of claims 1 to 3, characterized in that both the foot width of the indirectly cooled central rib (15), and the width of the resulting slit-like overflow channel parts (14 ') and (14 ") varies in the longitudinal direction
    [5]
    5. Cylinder head (1) according to one of claims 1 to 4, characterized in that the indirectly cooled central rib (15) has an at least approximately rectangular or trapezoidal-shaped cross-section.
    [6]
    6. Cylinder head (1) according to one of claims 1 to 5, characterized in that the overflow channel (14) from the pressure chamber (8) of the first stage to the suction chamber (10) of the second stage, wherein the sum of the volumes from the pressure chamber ( 8) of the first stage, intercooler (9) and second stage suction chamber (10) is greater than the first stage volume evacuated during a compression cycle. -6-
    类似技术:
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    同族专利:
    公开号 | 公开日
    CN103967755A|2014-08-06|
    CN103967755B|2017-08-15|
    AT512923B1|2013-12-15|
    US20140208938A1|2014-07-31|
    DE102014000226A1|2014-07-31|
    US9476421B2|2016-10-25|
    BR102014001958A2|2015-12-01|
    引用文献:
    公开号 | 申请日 | 公开日 | 申请人 | 专利标题
    DE2905720A1|1979-02-15|1980-08-28|Wabco Fahrzeugbremsen Gmbh|CYLINDER HEAD FOR MULTI-STAGE AIR PRESSER|EP2905191A1|2014-02-06|2015-08-12|Bendix Commercial Vehicle Systems LLC|Vehicle air compressor apparatus for a heavy vehicle air braking system|DE102005012202A1|2005-03-15|2006-09-28|Itg Kompressoren Gmbh|Cylinder head for a multi-stage piston compressor|US10578089B2|2017-03-30|2020-03-03|Eaton-Max, Inc.|Air compressor noise dampener|
    DE102017116870B3|2017-07-21|2019-01-24|Voith Patent Gmbh|Reciprocating engine with cooling device|
    法律状态:
    2020-09-15| MM01| Lapse because of not paying annual fees|Effective date: 20200125 |
    优先权:
    申请号 | 申请日 | 专利标题
    ATA50056/2013A|AT512923B1|2013-01-25|2013-01-25|Cylinder head for two-stage reciprocating compressor|ATA50056/2013A| AT512923B1|2013-01-25|2013-01-25|Cylinder head for two-stage reciprocating compressor|
    DE102014000226.8A| DE102014000226A1|2013-01-25|2014-01-09|Cylinder head for two-stage reciprocating compressor|
    CN201410026080.8A| CN103967755B|2013-01-25|2014-01-21|The cylinder head of the reciprocating-piston compressor of two-stage|
    US14/162,182| US9476421B2|2013-01-25|2014-01-23|Cylinder head for a two-stage reciprocating piston compressor|
    BR102014001958A| BR102014001958A2|2013-01-25|2014-01-27|cylinder head for a two stage reciprocating piston compressor|
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