• 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 reciprocating piston engine for a liquid or gaseous working medium, with at least one piston performing a straight-line reciprocating movement in a cylinder, which piston in the cylinder separates a first piston chamber from a second piston chamber, and with a reversing device which, in the two limit positions of the piston, alternately connects a feed line for the working medium to the first or second piston chamber. In order to simplify the construction and improve the functioning, the following features are proposed: a) the first piston chamber is connected to a first control chamber by way of a first flow line, whilst the second piston chamber is connected to a second control chamber by way of a second flow line; b) the two control chambers have a reversing valve, which in its one limit position in the first control chamber connects the said feed line to the first flow line and in the second control chamber connects the second flow line to a discharge line for the working medium at zero pressure, and which in its other limit position in the first control chamber interrupts the said connection between feed line and first flow line and at the same time connects the first flow line to the said discharge line and in the second control chamber interrupts the said connection between second flow line and discharge line and at the same time ... Original abstract incomplete.
    公开号:SU1551253A3
    申请号:SU884355098
    申请日:1988-02-04
    公开日:1990-03-15
    发明作者:Гольдин Рудольф
    申请人:Рудольф Гольдин (DE)；
    IPC主号:
    专利说明:

    FIG. one
    3155
    The invention relates to a hydraulic drive, namely to a hydraulic motor of reciprocating continuous movement.
    The aim of the invention is to improve the stability and reliability of switching.
    Fig. 1 shows the hydraulic motor in a position where its stem moves to the left; in fig. 2 - the same in the position corresponding to the movement of the rod to the right, i.e. after switching the switchgear.
    A piston 2 is mounted in cylinder 1 and is fixed on the rod 3, which divides the cylinder into two mutually variable cavities 4 and 5, the cavity 5 being connected
    through the pipeline 6 with a cavity
    7. On the rod 3, a driver 8 is mounted concentrically to it, which is connected with the possibility of relative movement with the cylinder 1 by means of a spring switch 9, made in the form of two or more evenly distributed springs pivotally connected to the driver and the cylinder.
    Each of the cavities (4,5-7) supply
    0
    five
    0 in the right position
    five
    and the stroke of the lead relative to valve x.
    The device works as follows.
    In the position shown in Fig. 1, the fluid flows under pressure from the pressure line 10 through the chamber 18, the open sealing valve 16 of the valve 14 into the cavity 7 and through the pipe 6 into the piston cavity 5. Under the pressure of the fluid, the piston 2 moves to the left. In this case, the fluid located in the cavity 4 is expelled through the internal cavity of the valve 15 and the gap in the area of the open seal 21 into the cavity 23 and then into the drain line 11. In this case, both valves 14 and 15 are in the extreme
    wherein their right sealing strips 20 and 17 are pressed against the respective walls of the annular chambers, as a result of which the cavity of the discharge line chamber 22 is cut off from the cavity 5, and the pressure line chamber 19 of the pressure line is cut off from cavity 4. The valves are in the right position due to two factors - action of spring switch, spring force
    on a distribution node, whose Q is constantly being transmitted through the end of a 35
    40
    connected to this cavity and alternately connecting or disconnecting it with pressure lines 10 and discharge 11.
    Each of the distribution units is made in the form of an annular chamber with a partition 12, 13, in the orifice of which, respectively, hollow annular valves 14, 15 are installed. The valves are axially displaced within the limits defined by the end walls of the chambers and arranged so that their end seals The larger diameters 16, 17 face the annular chambers 18, 19, i.e., the pressure line 10, which is permanently connected to the annular chambers. these cameras. The face sealing seams 20, 21 of smaller diameter are turned towards the annular chambers 22, 23, i.e. towards the drain line 11, which is permanently connected to these chambers. Both valves 14 and 15 are mounted on a leash 8 with the possibility of axial movement relative to it within the limits of x (Fig. 2). The total stroke of the driver relative to the stationary cylinder is L, which is the sum of the stroke of the valve within the annular chamber.
    45
    50
    levers 24, 25 of the driver 8 on the valves, as well as the pressure of the fluid acting on the valves in the axial direction. This hydraulic axial force arises due to the difference in diameters of sealing seals 26 and 21 of valve 14, the difference in the areas of which is acted upon by the pressure of cavity 5 (i.e. the driving pressure), as well as the diameters 17 and 27 of valve 15, the differential area of which pressure in the cavity of the chamber 19.
    When the piston moves to the left, its end edge 28 reaches the corresponding end of the driver, and the leader, together with the piston, moves to the left. In this case, the spring of the spring switch is compressed and the force from them no longer acts on the valves, but they remain in the same position due to the action of the above hydraulic forces pressing them to the right. When the end stops 29 and 30 of the leash 8 reach the corresponding valve stops, the latter are torn off by their end sealing edges (20 and 17) from the respective walls of the distribution chambers, due to
    Whose qin is transmitted through butt5
    0
    45
    50
    levers 24, 25 of the driver 8 on the valves, as well as the pressure of the fluid acting on the valves in the axial direction. This hydraulic axial force arises due to the difference in diameters of sealing seals 26 and 21 of valve 14, the difference in the areas of which is acted upon by the pressure of cavity 5 (i.e. the driving pressure), as well as the diameters 17 and 27 of valve 15, the differential area of which pressure in the cavity of the chamber 19.
    When the piston moves to the left, its end edge 28 reaches the corresponding end of the driver, and the driver together with the piston moves to the left. In this case, the spring of the spring switch is compressed and the force from them no longer acts on the valves, but they remain in the same position due to the action of the above hydraulic forces pressing them to the right. When the end stops 29 and 30 of the leash 8 reach the corresponding valve stops, the latter are torn off by their end sealing edges (20 and 17) from the respective walls of the distribution chambers, due to
    whereby the pressure in each of the distribution chambers on both sides of each valve is equalized and the hydraulic forces on the valves are no longer acting. However, now they are under pressure from the spring switch, since by this time it is already passing its middle position and its springs, straightening, pulling the leash 8, and with it through stops 29 and 30 - and valves 14, 15 to the left. Both valves, together with the driver, go to the left end position shown in FIG. 2.1
    Now the fluid from the pressure line enters the cavity 4, and from the cavity 5-7, the fluid is brought to the drain in the same way as described above. The piston moves to the right until the 2 end stop 31 of the rod 3 reaches the corresponding end 32 of the driver 8, and the valve switching process is repeated, as described above.
    In order to ensure the reliability of switching 2, it is necessary to provide a constructive condition in which the release of the valve of the drivers occurs already after the spring switch has passed its average position (the moment of maximum compression of the springs). This is provided at 0.5L.
    权利要求:
    Claims (2)
    [1]
    1. A reciprocating hydraulic motor comprising a cylinder with a piston disposed therein and a rod dividing the cylinder into two mutually variable cavities, each of which alternately connects 5
    0
    50
    five
    It is connected with a pressure or drain line by means of a distribution unit with a two-way switch, made in the form of a cylinder housing installed in the chamber and interacting with the annular partition of the valve block chamber, provided on both sides with end seals, each valve mounted concentrically on cylindrical a cage with the possibility of relative axial movement between the stops of the driver, and the latter is mounted with the possibility of axial movement relative to the rod, different Due to the fact that, in order to increase the stability and reliability of the switch, the two-way switch is spring-mounted and installed with the ability to interact with the driver and the cylinder, each valve is made in the form of a stepped bushing with end seals relative to the additional partition. the cylinder separating the pressure and drain lines, the valve diameter, which interacts with the additional partition, is made larger than the diameter of the sealing surface valve performance from the drain line, but smaller than the diameter of the girdle uplotnytelnogo by the pressure line.
    [2]
    2. The engine according to claim 1, characterized in that, in order to increase the reliability of switching valves, the x value of the axial movement of the valve relative to the driver, limited by its stops, is in the range from 0.5 to 1.0 from the full stroke L of the driver.
    类似技术:
    公开号 | 公开日 | 专利标题
    EP0304210B1|1992-11-25|Double diaphragm pumps
    EP0711905B1|2001-07-11|Improved mechanical shift, pneumatic assist pilot valve
    US5277555A|1994-01-11|Fluid activated double diaphragm pump
    US3540348A|1970-11-17|Fluid operated continuously actuated reciprocating piston drive
    SU1551253A3|1990-03-15|Hydraulic motor
    US5894781A|1999-04-20|Hydraulic hammer
    US3780622A|1973-12-25|Hydraulic oscillator and systems actuated thereby
    JPH11351422A|1999-12-24|Ball poppet pneumatic control valve
    US4397614A|1983-08-09|Unbalanced spool
    US3368458A|1968-02-13|Hydraulic motor
    EP0167635A1|1986-01-15|Hydraulic circuit for the control of reciprocating pistons pump
    JPH07269507A|1995-10-17|Accelerating device for hydraulic cylinder
    US5150643A|1992-09-29|Reciprocating actuator
    US2773486A|1956-12-11|Valve means for a fluid pressure system
    KR970075458A|1997-12-10|Self-pumped water-pneumatic buffer springs with internal leveling
    SU1165818A1|1985-07-07|Booster
    RU2084348C1|1997-07-20|Hydraulic press
    SU1765510A1|1992-09-30|Pneumatic pump
    JP3497549B2|2004-02-16|Pressure booster
    SU1143890A1|1985-03-07|Hydraulic drive
    RU2067695C1|1996-10-10|Fluid-pressure station
    RU2194196C2|2002-12-10|Autonomous hydraulic drive
    SU1327846A2|1987-08-07|Hydraulic drive for multisupport sprinkler cart
    SU1418516A1|1988-08-23|Hydraulic drive
    SU1753025A1|1992-08-07|Hydraulic reciprocate pump
    同族专利:
    公开号 | 公开日
    DE3703529A1|1988-08-25|
    DE3703529C2|1990-04-12|
    引用文献:
    公开号 | 申请日 | 公开日 | 申请人 | 专利标题
    US7663109B2|2006-12-14|2010-02-16|Tsinghua University|Mobile cantilever door-type container inspection system|
    RU2583568C2|2014-07-08|2016-05-10|Акционерное общество "Военно-промышленная корпорация "Научно-производственное объединение машиностроения" |Multiplier reverse mechanism with automatic control of reciprocating movement of working cylinder|US3218935A|1962-11-23|1965-11-23|Fluid Tec Company|Concrete finishing tool|
    US3374713A|1966-12-30|1968-03-26|Broughton Corp|Reciprocating fluid motor|
    DE1914408A1|1969-03-21|1970-10-08|Fichtel & Sachs Ag|Diaphragm spring friction clutch, especially for motor vehicles|
    DE2261323C3|1972-12-15|1975-07-03|Specken Ag, Zuerich |
    FR2358565B3|1976-07-16|1979-04-06|Dieny Alfred|DE3733596C2|1987-10-05|1991-10-24|Hau-Simex Giesserei- Und Oberflaechentechnik Vertriebsgesellschaft Mbh, 6050 Offenbach, De|
    WO1989008188A1|1988-03-03|1989-09-08|James Roderic Robertson|Linear reciprocating compressor|
    DE3921214C2|1989-06-28|1991-07-04|Wagner International Ag, Altstaetten, Ch|
    法律状态:
    优先权:
    申请号 | 申请日 | 专利标题
    DE19873703529|DE3703529C2|1987-02-06|1987-02-06|
    [返回顶部]