• 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:

    公开号:SU843718A3
    申请号:SU772476051
    申请日:1977-04-26
    公开日:1981-06-30
    发明作者:Бреннер Гейнц；Гамекерс Арно
    申请人:Боге Гмбх (Фирма)；
    IPC主号:
    专利说明:

    (54) SUPPORT WITH HYDRAULIC SUSPENSION FOR VEHICLE ENGINE
    with a gap forming the specified choke hole.
    In another form of implementation, channels are made in the form of grooves and holes between the bolt and the sleeve, connecting the main and additional chambers and forming the specified throttle opening.
    The partition is provided with an annular element in which said choke holes are made, while it is installed in the partition with a gap and the possibility of axial movement relative to the partition.
    One of the end walls is made double, consisting of a rigid outer wall forming the cavity, and an elastically inner wall compacted relative to it, leaning against the outer wall by means of elastic rubber protrusions.
    In addition, there is provided such an embodiment in which the cavity between the outer and inner wall is connected to the atmosphere by ventilation openings.
    One of the end walls can be covered with foam, and at least one of the end walls: ka is made with openings covered with elastic elements.
    FIG. 1 shows the engine mount with a circumferential wall in the form of a compression spring and a rigid partition; in fig. 2 - the same, with an elastic partition; in fig. 3 - engine support with an elastic partition made in one piece with the peripheral wall of the additional chamber; in fig. 4 vulcanized rubber-metal element before installation; in fig. 5- engine support, the end walls of which are double and connected by a central bolt; in fig. b - an embodiment of a double end wall of the support without a central bolt; Fig. 7 shows an embodiment of the end walls of the support; in fig. 8 - engine support with a disc-shaped ring element and a central bolt; in fig. 9 is a cross-section of a support with an annular element made in one piece with the partition; Fig, 10 - engine mount with an annular element without a central bolt, option; in fig. 11 support with an end wall of the main chamber, with openings covered with elastic elements; in fig. 12 end wall of the main chamber, top view.
    In the case of support (Fig. 1), the circumferential wall 1 of the main chamber along the outer circumference 2 is connected with the inner conical surface 3 provided with the flange 4 of the housing 5 and connected with the inner circumference 6
    with an outer conical surface 7 facing the motor end wall. The circumferential wall 8 of the additional chamber is connected along the outer circumference 9 with the inner conical surface 10 provided with the flange 11 of the housing 12 and circumferentially connected with the outer conical surface 14 with the end wall 15 rigidly and sealed between the flanges 4 and 11 by means of screws 16, the partition 17 separates on the one hand the main chamber 19 formed by the face 18 and the circumferential 1 and the additional chamber 20 formed by the circumferential wall 8 on the other side. The flanges 4 and 11 form the counter support 21, Continuous bo 22 fixes the end wall 15, the spacer sleeve 23 and the end wall 18 by means of a nut 24 and thus rigidly connects both end walls 15 and 18. The end wall 18 is connected through the extension rod 25 of the bolt 22 and the nut 26 to the engine housing 27.
    The counter 21 with its engine frame 28 is provided with screws 29. The partition 17 and the spacer 23 are installed with a clearance of 30. The Glan chamber 19 and the additional chamber 20 are filled with damping fluid. Consisting of 50% water and 50% glycol.
    When the motor housing 27 oscillates in the direction of the longitudinal axis of the bolt 22, the dynamic forces of the prop of the twin cylinder are perceived due to the elasticity of the circumferential walls 1 and 8, while the volumes of the main 19 and additional chambers 20 are changed, due to which the corresponding quantities of fluid are forced through the gap 30 and cause hydraulic damping forces.
    When performing the support (Fig. 2), the elastic circumferential wall 1 along the outer circumference 2 is connected with the inner conical surface 3 of the ring 31 and along the inner circumference 6 is connected with the outer conical surface 7 of the counter support 21. The elastic circumferential wall 8 around the outer circumference 9 is connected with the inner conical surface 10 of the ring 32 and around the inner circumference 13 - with the outer conical surface 14 of the welded-on element 33 of the counter support 21 The partition 17 is made elastic and connected to the inner casing 34 of the counter support 21 and the outer casing g 35, Elastic barrier 17 separates the main chamber 19 from the secondary chamber 2Q.
    权利要求:
    Claims (15)
    [1]
    The rings 31 and 32, together with the disks 36 and 37, form the end walls 18 and 15, the Remote sleeve 23 is made out of two parts, between which the sleeve 35 is clamped. The bolt 22 has circumferential grooves 38 and 39 and longitudinal grooves 40, 41 and 42 form the action as throttling openings between the main X1 of measure 19 and the additional chamber 20 connecting, channels, the size and shape of which determine the hydraulic damping of the engine mount. The bolt 22 has a hole 44 closed by a press-fit ball 43, through which fluid can be injected under pressure (with LAMNY or without increased pressure relative to the environment. A vent hole (not shown) can be placed anywhere. A cavity 45 is provided in the main chamber used for filling with gas and closed by a membrane 46. This version of the support works in the same way as the first one.When performing the support (Fig. 3), the elastic circumferential wall 1 is connected to the inner conical surface 3 of the end wall 18 and to the outer conical surface 3. The casing surface 47 of the counterholds 21. The elastic circumferential wall 8 is made in one piece with the partition 17 and is connected with the inner surface 10 of the end wall 15 remote from the engine, with the outer surface 14 of the sleeve 35 and with the inner conical surface 48 of the counter support 21. Dis, with sleeve 35, a trench sleeve 23 forms a throttle gap 49, the shape and dimensions of which mainly determine the magnitude of the damping forces. (Engine support is shown in the unloaded condition). When the engine weight is applied, the end face distance decreases. the legs 18 are from the counter support 21. From this supposed static initial position, the engine support is free to move in both directions. In one direction, to the stop of the end wall 18, in the protrusion 50 and in the other direction, to the stop, in the end wall 15, to the protrusion 51. . The protrusion 50 is located on the side of the end face 52 of the ring 47 and creates a rather rigid stop of the end wall 18. The protrusion 51 is located in the area of the sleeve 35 and creates a soft stop of the end wall 15, and, in this direction, the partition 17 works as a compression spring. The rubber-metal element (Fig. 4) before installation has an axial length a, which is longer than the corresponding axial length in the engine mounts (Fig. 3) after installation, so that the circumferential wall 1 and the circumferential wall 8 after installation have directed to each other preliminary pressure The voltage value is given by the length of the spacer 23, due to which the support characteristic is required. When the support (Fig. 5) is made, the end walls are made double, the rings 31 and 32 fasten the outer and inner walls to each other by means of the bolts 53 and 54. The outer walls 55 and 56 have ventilation holes 57, and the inner walls are rubber-metal elements consisting of inner metal rings 58 and 59, outer metal rings 60 and 61, and metal discs 62 and 63, vulcanized into rubber discs 64 and 65 which have annular bulges 66, 67, 68 and 69. The elastic partition is made with a neck 70 reinforced with a metal gasket. The gap 30 between the spacer 23 and the neck 70 serves as a throttle bore. FIG. 6 shows an embodiment of a double end wall of a support that does not have a central bolt. In this case, the outer wall is provided with a pin 71, and a rigid connection between the end walls of the main and additional chambers can be carried out through C-shaped elements (Fig. 10). The inner wall at the same time SCX; toit from a metal disk 72 and the surrounding rubber bead 73, fastened to the outer wall 55 by flanging 54. The rubber bead 73 has an annular thickening 74, besides that the disk 72 may have elastic protrusions 75. In FIG. 7 shows an embodiment of the end walls of the support in which the inner surfaces of the end walls 15 and 18 are covered with a layer 76 of foam. When performing the support (Fig. 8), it does not have a spacer and a connecting bolt, their role in this case is performed by the connecting stud 77, having shoulders 78 and 79, which provide a rigid connection between the end walls 15 and 18. The partition 17 is made with an annular groove 80, which has an elastic end surface 81 and a rigid end surface 82 formed by a washer 83 fixed in the partition. In this groove there is a flexible annular element movable in all directions having an intermediate wall 85 sec. iem 86 through which the connecting pin 77. The inner surface 87 has openings 86 arcuate profile which is relatively -easy deformed transversely in the interaction with the pin 77. The clearance between the annular member and the pin 77 serves as a throttle opening. FIG. 9 shows a variant with an annular element 84, made in one piece with the partition 17 and connected with it by means of a thin flange 88. When the support (FIG. 10) is performed, the end walls 15 and 18 are provided with pins 71, made with them in one piece, and the rigid connection of these strings to each other is carried out by C-about various elements 89. The ring element is made in the form of a metal ring 90, having flanges 91 and 92 with which the elastic intermediate wall 85 is adhesionally connected with the throttle gap 49, y. Which / edge 93 faces the main chamber 19 , is made sharp, and the edge 94, facing the additional chamber 20, is rounded. The annular element is installed with a gap in the bulkhead 17 with possible axial movement, which is limited by the end faces of surfaces 95 and 96 of the bulkhead 17. Counter bearing 21 is connected to the engine frame (not shown). In the embodiment of the support (FIGS. 11 and 12), the end wall 18 of the main chamber 19 has openings 97 and consists of a rim 98 and four spokes 99. The openings 97 are covered with a membrane 100 of elastic material that covers the spokes on both sides, the course of the membrane is limited The washer 101 installed between the engine casing 27 and the end wall 18 The end wall 15 of the additional chamber 20 has openings 102 that are covered with a layer 76 of foam plastic. The circumferential wall 1 is made thicker, than the circumferential wall 8, and defines the main bearing force of the support. The circumferential wall. 8 provides the same change in the volume of the main 19 and additional 20 chambers when moving, the end walls 15 and 18. Thus, the occurrence of a vacuum in one of the chambers is prevented, and, consequently, the emergence of empty spaces in the liquid, which is accompanied shm Claim 1 ,. A hydraulic damping support for the vehicle’s engine, primarily a car, containing the main and auxiliary chambers, the first of which is limited by an end wall connected to the engine block, the circumferential wall made as a compression spring, and one side of the counter support, limiting On the other hand, there is an additional chamber with elastic walls. both chambers are connected by means of a throttle hole, in order to increase the gcortisation and damping effect, the additional chamber is provided with a metal end wall having a conical surface and rigidly connected to the end wall of the main chamber, the circumferential wall of the additional chamber is designed as a compression spring and the counter support is made in the form of a flange of the engine frame with inner and outer conical surfaces,
    [2]
    2. A support according to claim 1, characterized in that the circumferential wall of the additional chamber adhesion i is associated with the conical surfaces of the end wall and the counterpore.
    [3]
    3. Support pop. 2, in contrast to the fact that the end wall of the additional chamber is rigidly connected to the end wall of the main chamber by means of a bolt with a spacer sleeve.
    [4]
    4. Support on p. 3, about t l. and that the partition is made of an elastic material.
    [5]
    5. A support according to claim 4, wherein the spacer sleeve is made of two parts, between which there is a sleeve, with which the partition is adhesively connected.
    [6]
    6. The support according to claim 4, distinguished by the fact that the circumferential wall of the additional chamber is made in one piece with the partition.
    [7]
    7. The support according to claim 3, characterized by the fact that the spacer sleeve and the partition are installed with a gap.
    [8]
    8. The support according to claim 4, characterized by the fact that the partition is made with a flange, the spacer sleeve and the flange being installed with a gap, forming a specified choke hole.
    [9]
    9. Support according to claim 5, characterized by the fact that between the bolt and the sleeve are made channels in the form of grooves and holes connecting the main and additional chambers and forming the specified throttle hole. .
    [10]
    10. A support according to claim 4, wherein the partition is provided with an annular element in which said choke holes are made, and which is mounted with the possibility of axial movement relative to the partition.
    [11]
    11. Support pop 10, characterized in that the annular element is installed in the partition with a gap.
    [12]
    12. A support according to claim 3, characterized in that one of the end walls is double, consisting of a rigid outer wall forming the cavity and an elastic inner wall which is compacted relative to it and resting on the outer wall by means of elastic rubber protrusions. .
    [13]
    13. Support pop, 12, characterized in that the cavity between the outer and the inner wall is connected with the atmosphere by ventilation openings.
    [14]
    14. Support according to claim 3, of which is one of the fact that one of the end walls is covered with foam.
    [15]
    15. Support on PP. 1-14, different from this, that at
    33
    , IS m with n p; K g
    fS
    3 One end wall is made with swarms, which are covered with elastic elements. Priority points: 27.04 ..76 on PP. 1-7 and 9; 10/19/756 8 and 14; 10.27.76 on PP. 12 and 13; 03/23/37 in paragraphs 10 and llj 03/24/37 in accordance with clause 15. Sources of information that are taken into account during examination 1. Patent of Germany 945899, 63 C 40, 1956.
    /
    "
    / go years
    类似技术:
    公开号 | 公开日 | 专利标题
    SU843718A3|1981-06-30|Bearing with hydraulic damping for engine of transport device
    US4871150A|1989-10-03|Elastically yieldable support in particular for the suspension of a vehicle engine
    US4700934A|1987-10-20|Pretensionable and hydraulically damped mounting element
    US4998345A|1991-03-12|Method of manufacturing fluid-filled elastic mount having pressure-receiving and equilibrium chambers
    US4630803A|1986-12-23|Suspension-strut mounting for installation between a shock-absorber strut or spring strut and a vehicle body spring-supported with respect to the axles, in particular of a motor vehicle
    US4161304A|1979-07-17|Rubber elastic engine mounts or supports with hydraulic damping, especially for engine suspensions in motor vehicles
    US4401298A|1983-08-30|Flexible column viscous spring damper
    US3625321A|1971-12-07|Shock absorber and fluid-compensating means
    US3856287A|1974-12-24|Piston rod seal for adjustable pneumatic spring
    US4364457A|1982-12-21|Piston-cylinder unit particularly for shock absorber or compression strut
    US5456454A|1995-10-10|Support bearing for automotive vehicles
    US4342446A|1982-08-03|Self-leveling viscous elastic damper
    JP2984863B2|1999-11-29|Hydraulic buffer silent block
    US4787610A|1988-11-29|Vibration isolating devices
    US4893798A|1990-01-16|Fluid-filled elastic bushing having means for limiting elastic deformation of axial end portions of elastic member defining pressure-receiving chamber
    JPH0724674Y2|1995-06-05|Upper support for suspension
    US20030155697A1|2003-08-21|Dynamic damper and propeller shaft
    JP2000186739A|2000-07-04|Fluid seal type vibration control device
    US6616130B2|2003-09-09|Cylindrical vibration-isolating device
    US4919401A|1990-04-24|Fluid-filled bushing having radially displaceable intermediate sleeve coated with sealing rubber layer
    US4809959A|1989-03-07|Hydraulic antivibratory supports
    US6799753B2|2004-10-05|Fluid-filled elastic mount
    US4854561A|1989-08-08|Elastic bushing filled with viscous fluid
    US5280885A|1994-01-25|Vibration isolating apparatus
    JP4131410B2|2008-08-13|Method for manufacturing fluid-filled cylindrical mount
    同族专利:
    公开号 | 公开日
    GB1583965A|1981-02-04|
    NL7704545A|1977-10-31|
    DD129760A5|1978-02-08|
    NL167017C|1981-10-15|
    CA1053642A|1979-05-01|
    AR212993A1|1978-11-30|
    BR7702629A|1978-02-28|
    GB1583964A|1981-02-04|
    MX4249E|1982-03-02|
    IT1125741B|1986-05-14|
    AU2457077A|1978-11-02|
    SE7704780L|1977-10-28|
    GB1583963A|1981-02-04|
    AU501777B2|1979-06-28|
    引用文献:
    公开号 | 申请日 | 公开日 | 申请人 | 专利标题
    RU2677804C2|2015-10-27|2019-01-21|Форд Глобал Текнолоджиз, Ллк|Method of controlling dual-state vacuum switchable mount|
    RU2717876C2|2017-04-04|2020-03-26|Форд Глобал Текнолоджиз, Ллк|System and method for diagnosing active engine support|
    IT1150821B|1982-04-09|1986-12-17|Gomma Antivibranti Applic|CUSHIONING SUPPORT|
    ES274469Y|1982-10-28|1984-08-16|Continental Gummi-Werke Aktiengesellschaft|HYDRAULICALLY CUSHIONED ELASTIC SUPPORT, ESPECIALLY FOR THE PROPELLER MOTOR IN AUTOMOBILE VEHICLES|
    DE3233456C2|1982-09-09|1987-04-09|Continental Gummi-Werke Ag, 3000 Hannover, De|
    US4641817A|1983-04-05|1987-02-10|Dunlop Limited|Vibration absorbing mountings|
    GB2149880B|1983-11-12|1987-05-28|Dunlop Ltd|Vibration absorbing mountings|
    GB8622638D0|1986-09-19|1986-10-22|Dunlop Ltd|Elastomeric mounting|
    US4915365A|1987-09-04|1990-04-10|The Standard Products Company|Elastomeric engine mount with hydraulic damping|
    DE3917586C1|1989-05-30|1990-12-20|Metzeler Gmbh, 8000 Muenchen, De|
    GB2298021B|1995-02-17|1997-02-12|Barry Controls|Improved vibration isolator|
    GB2504477B|2012-07-27|2015-08-26|Caterpillar Ni Ltd|Base and Mounting Means for a Generator|
    法律状态:
    优先权:
    申请号 | 申请日 | 专利标题
    DE2618333A|DE2618333C3|1976-04-27|1976-04-27|Two-chamber engine mount with hydraulic damping|
    DE19762647105|DE2647105A1|1976-10-19|1976-10-19|Hydraulic twin cell elastic walled engine mounting - has small holes in inter cell plate fixed to engine and chassis via main cell|
    DE19762648526|DE2648526C3|1976-10-27|1976-10-27|Two-chamber engine mount|
    DE19772718121|DE2718121C3|1977-03-23|1977-03-23|Two-chamber engine mount with hydraulic damping|
    DE19772713008|DE2713008C3|1977-03-24|1977-03-24|Rubber elastic engine mount with hydraulic damping|
    [返回顶部]