WO2015149207A1 - 一种转向电机的减震机构 - Google Patents

一种转向电机的减震机构 Download PDF

Info

Publication number
WO2015149207A1
WO2015149207A1 PCT/CN2014/074346 CN2014074346W WO2015149207A1 WO 2015149207 A1 WO2015149207 A1 WO 2015149207A1 CN 2014074346 W CN2014074346 W CN 2014074346W WO 2015149207 A1 WO2015149207 A1 WO 2015149207A1
Authority
WO
WIPO (PCT)
Prior art keywords
oil
cavity
cylinder
elastic
steering motor
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.)
Ceased
Application number
PCT/CN2014/074346
Other languages
English (en)
French (fr)
Inventor
龚蜀刚
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.)
SHENZHEN ZHIXING SINGLE-AXLE TWO-WHEELED DRIVING TECHNOLOGY Co Ltd
Original Assignee
SHENZHEN ZHIXING SINGLE-AXLE TWO-WHEELED DRIVING TECHNOLOGY Co Ltd
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 SHENZHEN ZHIXING SINGLE-AXLE TWO-WHEELED DRIVING TECHNOLOGY Co Ltd filed Critical SHENZHEN ZHIXING SINGLE-AXLE TWO-WHEELED DRIVING TECHNOLOGY Co Ltd
Priority to US15/300,534 priority Critical patent/US10348154B2/en
Priority to ES14888401T priority patent/ES2794086T3/es
Priority to JP2016559977A priority patent/JP6386078B2/ja
Priority to KR1020167028554A priority patent/KR102128148B1/ko
Priority to PCT/CN2014/074346 priority patent/WO2015149207A1/zh
Priority to EP14888401.8A priority patent/EP3128652B1/en
Priority to CN201480076951.5A priority patent/CN106104983B/zh
Priority to EP14887872.1A priority patent/EP3127778B1/en
Priority to US15/300,691 priority patent/US10348155B2/en
Priority to KR1020167028405A priority patent/KR102128146B1/ko
Priority to CN201480076947.9A priority patent/CN106488868B/zh
Priority to JP2016559975A priority patent/JP6386076B2/ja
Priority to PCT/CN2014/074600 priority patent/WO2015149296A1/zh
Priority to PL14887872T priority patent/PL3127778T3/pl
Priority to ES14887872T priority patent/ES2750554T3/es
Publication of WO2015149207A1 publication Critical patent/WO2015149207A1/zh
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

Links

Classifications

    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02K—DYNAMO-ELECTRIC MACHINES
    • H02K5/00—Casings; Enclosures; Supports
    • H02K5/24—Casings; Enclosures; Supports specially adapted for suppression or reduction of noise or vibrations
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B62—LAND VEHICLES FOR TRAVELLING OTHERWISE THAN ON RAILS
    • B62D—MOTOR VEHICLES; TRAILERS
    • B62D5/00—Power-assisted or power-driven steering
    • B62D5/04—Power-assisted or power-driven steering electrical, e.g. using an electric servo-motor connected to, or forming part of, the steering gear
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B62—LAND VEHICLES FOR TRAVELLING OTHERWISE THAN ON RAILS
    • B62D—MOTOR VEHICLES; TRAILERS
    • B62D5/00—Power-assisted or power-driven steering
    • B62D5/04—Power-assisted or power-driven steering electrical, e.g. using an electric servo-motor connected to, or forming part of, the steering gear
    • B62D5/0418—Electric motor acting on road wheel carriers
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B62—LAND VEHICLES FOR TRAVELLING OTHERWISE THAN ON RAILS
    • B62D—MOTOR VEHICLES; TRAILERS
    • B62D7/00—Steering linkage; Stub axles or their mountings
    • B62D7/02—Steering linkage; Stub axles or their mountings for pivoted bogies
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B62—LAND VEHICLES FOR TRAVELLING OTHERWISE THAN ON RAILS
    • B62D—MOTOR VEHICLES; TRAILERS
    • B62D7/00—Steering linkage; Stub axles or their mountings
    • B62D7/22—Arrangements for reducing or eliminating reaction, e.g. vibration, from parts, e.g. wheels, of the steering system
    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02K—DYNAMO-ELECTRIC MACHINES
    • H02K5/00—Casings; Enclosures; Supports
    • H02K5/04—Casings or enclosures characterised by the shape, form or construction thereof
    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02K—DYNAMO-ELECTRIC MACHINES
    • H02K7/00—Arrangements for handling mechanical energy structurally associated with dynamo-electric machines, e.g. structural association with mechanical driving motors or auxiliary dynamo-electric machines
    • H02K7/14—Structural association with mechanical loads, e.g. with hand-held machine tools or fans
    • H02K7/16—Structural association with mechanical loads, e.g. with hand-held machine tools or fans for operation above the critical speed of vibration of the rotating parts

Definitions

  • the invention relates to the technical field of hydraulic shock absorption, in particular to a shock absorbing mechanism of a steering motor.
  • the steering system of the automobile has also been rapidly improved, and the electric power steering system is the development direction of the automobile steering system.
  • the system provides steering assistance directly from the steering motor, eliminating some of the components necessary in traditional hydraulic power steering systems, saving energy and protecting the environment.
  • the system is easy to adjust, flexible to assemble, and in a variety of situations.
  • the steering assist can be provided underneath.
  • the torque sensor detects the steering of the steering wheel and the magnitude of the torque, and sends the voltage signal to the electronic control unit.
  • the electronic control unit detects the torque voltage signal and the direction of rotation according to the torque sensor. And the vehicle speed signal, etc., an instruction is given to the steering motor controller to cause the steering motor to output a steering assist torque of a corresponding magnitude and direction to generate auxiliary power; when the vehicle is not turning, the electronic control unit does not issue an instruction to the motor controller, the motor Not working.
  • a damping system is arranged inside the steering motor, and the conventional damping system uses a carbon brush and a collecting ring.
  • the damping system continuously buffers the vibration.
  • the carbon brush and the collector ring are continuously rubbed, so that it is easily damaged by friction, and it is sensitive to temperature, and is easily damaged by temperature difference, which seriously affects the stability and life of the steering motor. .
  • An object of the present invention is to provide a damper mechanism for a steering motor, which aims to solve the problem of structural wear and tear caused by constant friction between components in a cylinder assembly in a damper system of a conventional steering motor in the prior art, and Temperature variations cause structural damage and defects that affect the stability and service life of the steering motor.
  • the technical solution provided by the present invention is a shock absorbing mechanism of a steering motor, which is disposed in the steering motor, and the shock absorbing mechanism includes an upper cover buffer assembly, and a oil separation plate disposed under the upper cover buffer assembly.
  • the oil separation plate and the upper cover buffer assembly are closed to form a sealed axial cavity;
  • a cylinder assembly is fixed under the oil separation plate, and the cylinder assembly includes an oil cylinder open at both ends, and is disposed in the oil cylinder
  • an elastic oil bladder having an opening at an upper end, the upper end of the elastic oil bladder is fixedly connected to the inner wall of the cylinder, and communicates with the axial cavity, and the cylinder is further provided with a piston sliding along the axial direction of the cylinder, The piston is coupled to the lower end of the elastomeric oil bladder.
  • the upper cover buffer assembly includes an upper cover and a buffer assembly
  • the buffer assembly includes an elastic body, an elastic spacer and an elastic diaphragm which are sequentially stacked in the axial cavity, and an edge of the elastic diaphragm The inner lower edge of the upper cover is embedded and fastened to the inner wall of the axial cavity to form a closed.
  • a damping hole is disposed in the lower end of the oil separation plate, and the damping hole is disposed for the upper end of the elastic oil bladder, and communicates with the axial cavity and the elastic oil bladder, respectively.
  • the diameter of the orifice is smaller than the diameter of the opening of the upper end of the elastic oil bladder.
  • the elastic diaphragm has a butterfly shape, and the oil separation disc is sealed with the upper cover buffer assembly by a fastener.
  • the oil separation plate is provided with an oil passage arranged in a radial direction and communicating with the axial cavity, and the oil separation plate is provided with an oil inlet port, and the oil separation plate is respectively upwardly Extending downwardly, there is a hollow column having an inner cavity arranged in the axial direction, and an inner wall of the hollow column is provided with an oil passage communicating with the oil passage.
  • a inner side of the hollow column is provided with a reversing valve having a valve core, and an inner side wall of the hollow column forms a first radial cavity with an outer wall of the reversing valve, the first radial type a pin is embedded in the cavity, and the first radial cavity is separated by the pin to form mutually independent oil-inlet oil inlet cavity and oil-distribution disk oil-extracting cavity, and the oil-distributing disk inlet oil cavity and the oil-distributing disk
  • the oil inlet port is connected, and the oil discharge cavity of the oil separation plate is in communication with the axial cavity;
  • the upper part of the side wall of the valve cavity is provided with a reversing valve oil passage arranged radially in the radial direction, and the oil passage of the reversing valve is disposed below the axial direction of the oil passage;
  • the outer wall of the upper end of the valve core is provided with a semi-circular oil passage groove having a semicircular cross section, and the oil passage ring communicates with the oil inlet oil inlet cavity and the oil discharge oil outlet cavity;
  • An outer wall of the lower end of the valve core and a lower side wall of the valve cavity form a second radial cavity, and a lower portion of the valve cavity is provided with an oil outlet, and the oil outlet is in communication with the second radial cavity.
  • the reversing valve further includes a winding coil disposed under the oil separation disc and sleeved on an outer circumference of the valve chamber.
  • the damper mechanism includes a plurality of the cylinder assemblies, each of the cylinder assemblies being disposed below the oil slinger and circumferentially disposed within the steering motor.
  • the shock absorbing mechanism of the steering motor provided by the invention adopts an elastic oil bladder in the cylinder assembly and seals the elastic oil bladder with the cavity, thereby overcoming the friction caused by the conventional hydraulic shock absorption system.
  • the problem of component damage and temperature-sensitive defects prolongs the service life of the shock absorbing mechanism and saves costs.
  • FIG. 1 is a schematic cross-sectional view showing a shock absorbing mechanism applied to a steering motor according to an embodiment of the present invention
  • Figure 2 is a partial enlarged view of Figure 1;
  • Figure 3 is a partial enlarged view of the portion of the oil separation plate of Figure 1;
  • Figure 4 is a partially enlarged schematic view of the portion of the reversing valve of Figure 1;
  • Figure 5 is a cross-sectional view taken along the line A-A of Figure 1;
  • Figure 6 is a cross-sectional view taken along the line B-B of Figure 1.
  • the embodiment provides a shock absorbing mechanism of a steering motor, which is disposed inside the steering motor, and includes: an upper cover buffer assembly 1, an oil separation plate 2, and a cylinder assembly 5, wherein the oil separation plate 2 is disposed Below the upper cover buffer assembly 1, and the upper cover buffer assembly 1 and the oil separation plate 2 are closed to form a sealed axial cavity 4, which is provided with oil for buffering vibration.
  • the buffer assembly 11; the cylinder assembly 5 is fixedly disposed under the oil separation plate 2, the cylinder assembly 5 includes an oil cylinder 51, an elastic oil bladder 52 and a piston 53, the oil cylinder 51 has openings at both ends thereof, and the elastic oil bladder 52 and the piston 53 are disposed
  • the elastic oil bladder 52 is a bladder-shaped elastic diaphragm having an open upper end, and an edge of the upper end of the elastic oil bladder 52 is fixedly coupled to an inner wall of the upper end of the cylinder 51, thereby forming a seal to the opening of the upper end of the cylinder 51, and The opening of the upper end of the elastic oil bladder 52 communicates with the axial cavity 4.
  • the piston 53 is fixedly coupled to the lower end of the elastic oil bladder 52, and the piston 53 is axially slidable along the inner cavity of the cylinder 51 in the cylinder 51.
  • the piston 53 slides up and down in the cylinder 51 as the steering motor vibrates, and the elastic oil bladder 52 is pulled or compressed by sliding thereof.
  • the elastic oil bladder 52 is compressed, the elastic oil bladder The oil in 52 is squeezed and flows into the axial cavity 4, and then the oil compresses the buffer assembly 11 to cause it to elastically deform, thereby achieving buffer shock, when the elastic oil bladder 52 is stretched, the axial direction
  • the oil in the cavity 4 will flow back into the elastic oil bladder 52, and the cushioning assembly 11 will return to deformation.
  • the above-mentioned shock absorbing mechanism is used for buffer damping of the steering motor, and has the following characteristics:
  • the upper cover buffer assembly 1 and the oil separation plate 2 are closed to form a sealed axial cavity 4, and a cylinder assembly 5 abutting the axial cavity 4 is disposed on the lower side of the oil separation plate 2, through the cylinder assembly 5
  • the elastic oil bladder 52 is in sealing communication with the axial cavity 4, and the elastic oil bladder 52 overcomes the wear and tear of the components of the cylinder assembly 5 of the conventional hydraulic shock absorbing mechanism, and the temperature-sensitive defect prolongs the service life of the shock absorbing mechanism. Save costs.
  • the upper cover buffer assembly 1 includes an upper cover 12 and a buffer assembly 11.
  • the purpose of the buffer assembly 11 is to achieve buffer damping by elastic deformation thereof.
  • the buffer assembly 11 includes an elastic body 111, The elastic spacer 112 and the elastic diaphragm 113, wherein the elastic body 111, the elastic spacer 112 and the elastic diaphragm 113 are sequentially stacked in the axial cavity 4 from top to bottom, and the edge of the elastic diaphragm 113 is embedded inside the upper cover 12.
  • the lower edge is fixedly connected to the inner wall of the axial cavity 4 and forms a seal, so that the elastic body 111 and the elastic spacer 112 are sealed by the elastic diaphragm 113 in the cavity formed by the inner wall of the axial cavity 4 and the elastic diaphragm 113.
  • the elastic body 111 and the elastic spacer 112 can be moved in the chamber.
  • the buffer assembly 11 can also be other forms of buffer structure according to actual conditions and needs.
  • a damping hole 26 is disposed in a bottom surface of the lower end of the oil separation plate 2, and the damping hole 26 is disposed at an opening of the upper end of the elastic oil bladder 52.
  • the elastic oil bladder 52 is formed with the axial cavity 4 through the damping hole 26.
  • the elastic oil bladder 52 may also be in sealing communication with the axial cavity 4 in other manners, such as pipe communication, or passage communication.
  • the diameter of the orifice 26 is smaller than the diameter of the opening of the upper end of the elastic oil bladder 52.
  • the cavity 4 which acts as a damping buffer, of course, is only one form of cushioning, and in other embodiments, other cushioning forms may be used.
  • the elastic diaphragm 113 has a butterfly shape.
  • the structure of the oil separation disc 2 corresponds to the structure of the upper cover buffer assembly 1, and the two covers are combined to form a sealed connection by a fastener.
  • the above-mentioned upper cover buffer assembly 1 and the above oil separation plate 2 may also have other forms of structure, depending on the specific circumstances and actual needs.
  • a hollow column 21, an oil inlet port 22, and an oil passage 23 arranged in the radial direction and communicating with the axial cavity 4 are disposed in the oil separation plate 2, An oil passage is opened on the inner wall of the hollow column 21, and the inner cavity of the hollow column 21 communicates with the oil passage 23 through the oil passage.
  • the inner side of the hollow column 21 is provided with a reversing valve 3, and the reversing valve 3 has a valve core 31 and a valve chamber 32; the inner wall of the hollow column 21 and the outer wall of the valve chamber 32 form a first radial cavity, the first radial type A pin 6 is embedded in the cavity, and the first radial cavity is separated by the pin 6 to form two mutually independent radial cavities, one of which is an oil-input oil-inducing cavity 24, and the oil-distributing disk oil-injecting cavity 24 is The oil inlet 22 is connected.
  • the first radial cavity formed by the inner cavity side wall of the hollow column 21 and the outer wall of the valve cavity 32 is separated from the other radial cavity formed by the pin 6 embedded therein. That is, the oil-discharging oil-discharging cavity 25 is connected to the axial-shaped cavity 4; the reversing valve oil-passing passage 33 is arranged in the upper part of the side wall of the valve cavity 32. a radially disposed oil passage hole 34 is disposed below the axial direction of the reversing valve oil passage 33.
  • the upper ring of the outer wall of the valve core 31 is provided with a semicircular oil passage groove 35 having a semicircular cross section.
  • the oil ring groove 35 respectively communicates with the oil inlet oil inlet cavity 24 and the oil separation plate oil discharge cavity 25; a second radial cavity 36 is formed between the outer wall of the lower end of the valve core 31 and the lower inner wall of the valve cavity 32, and the valve cavity 32 An oil outlet 37 is opened in the lower portion, and the oil outlet 37 communicates with the second radial cavity 36.
  • the oil enters the route from the oil inlet port 22 into the oil inlet oil inlet cavity 24, through the oil passage of the reversing valve oil passage 33 and the oil ring groove 35, and the oil flow passes through the oil distribution plate.
  • the oil cavity 25 enters the axial cavity 4 and then passes through the orifice 26 into the elastic oil bladder 52.
  • the oil passage 34 and the second diameter are realized.
  • the communication or blocking of the cavity 36 further realizes the communication or blocking of the oil-inlet oil inlet cavity 24 and the axial cavity 4 described above.
  • other components or methods may be used to control the on and off of the oil in the oil passage.
  • the directional control valve 3 is an electromagnetic directional control valve, and the directional control valve 3 further includes a winding coil 39.
  • the valve chamber 32 is disposed on the inner wall of the upper portion of the hollow column 21, and the winding coil 39 is sleeved.
  • the outer wall of the valve chamber 32 is provided with an axial positioning flange, the winding coil 39 is located below the hollow column 21 and above the outer wall positioning flange of the valve chamber 32.
  • other types of reversing valves may be employed depending on the actual situation and needs.
  • the oil ring groove 35 and the oil passage 23 are staggered, and the switching valve oil passage 33 is blocked by the outer wall of the valve core 31.
  • the second radial cavity 36 passes through the oil hole 34 and the minute.
  • the oil pan inlet oil chamber 24 communicates, that is, the oil passage formed by the oil disc inlet oil chamber 24 and the second radial cavity 36 constitutes a passage, and the oil disc inlet oil chamber 24 and the axial cavity 4 are The oil passage formed by the elastic oil bladder 52 is blocked; when the winding coil 39 is energized, the valve core 31 is entirely moved downward, the oil passage groove 35 is in alignment with the oil passage 33, and the O-ring of the lower tapered surface of the valve core 31 is sealed.
  • the ring 38 presses the conical surface of the lower portion of the valve chamber 32, that is, the second radial cavity 36 is blocked; thus, the oil passage of the oil inlet chamber 24 and the axial cavity 4 and the elastic oil bladder 52 are formed.
  • the passage is formed, and at the same time, the oil passage formed by the oil inlet cavity 24 and the second radial cavity 36 is blocked; the switching of the two paths is realized by the switching of the switching valve 3, and mutual Do not interfere.
  • each group of cylinder assemblies 5 are disposed in the damper mechanism, and each group of cylinder assemblies 5 are disposed under the oil slinger 2, and the upper ends of each group of cylinder assemblies 5 are offset from the bottom surface of the oil slinger 2.
  • each of the elastic oil bladders 52 of each group of cylinder assemblies 5 communicates with the axial cavity 4 through respective corresponding orifices 26.
  • each group of cylinder assemblies 5 is circumferentially disposed inside the steering motor.
  • the number of cylinder assemblies 5 can be determined on a case-by-case basis, and each set of cylinder assemblies 5 can also be distributed in other forms.

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Transportation (AREA)
  • Mechanical Engineering (AREA)
  • Power Engineering (AREA)
  • Power Steering Mechanism (AREA)
  • Fluid-Damping Devices (AREA)
  • Combined Devices Of Dampers And Springs (AREA)
  • Vibration Dampers (AREA)
  • Multiple-Way Valves (AREA)
  • Steering-Linkage Mechanisms And Four-Wheel Steering (AREA)
  • Magnetically Actuated Valves (AREA)
  • Motor Or Generator Cooling System (AREA)

Abstract

一种转向电机的减震机构，包括上盖缓冲组件（1），置于上盖缓冲组件（1）的下方的分油盘（2），该分油盘（2）与上盖缓冲组件（1）盖合形成密封的轴向型腔（4）；分油盘（2）的下方固设有油缸组件（5），该油缸组件（5）包括两端开口的油缸（51），设于油缸（51）中且上端具有开口的弹性油囊（52），该弹性油囊（52）的上端与油缸（51）内壁固定连接，且该弹性油囊（52）的上端连通轴向型腔（40），在油缸（51）内还设有沿油缸（51）轴向滑动的活塞（53），该活塞（53）连接于弹性油囊（52）下端。该转向电机的减震机构，克服了传统液压减震系统中因摩擦导致构件损坏的问题，及对温度敏感的缺陷，延长了减震机构的使用寿命。

Description

一种转向电机的减震机构 技术领域
本发明涉及液压减震的技术领域，尤其涉及一种转向电机的减震机构。
背景技术
随着汽车工业的不断发展，汽车的转向系统也得到飞速进步，而电动助力转向系统则是汽车转向系统的发展方向。该系统由转向电机直接提供转向助力，省去了传统液压动力转向系统中所必需的一些部件，既节省能量，又保护了环境；另外，该系统还具有调整简单、装配灵活以及在多种状况下都能提供转向助力的特点。
驾驶员在操纵方向盘进行转向时，转矩传感器检测到转向盘的转向以及转矩的大小，将电压信号输送到电子控制单元，电子控制单元根据转矩传感器检测到的转矩电压信号、转动方向和车速信号等，向转向电机控制器发出指令，使转向电机输出相应大小和方向的转向助力转矩，从而产生辅助动力；当汽车不转向时，电子控制单元不向电动机控制器发出指令，电动机不工作。
为了克服不良路况对转向电机产生震动的影响，在转向电机内部设置有减震系统，而传统的减震系统中采用了碳刷和集电环，转向电机震动时，减震系统不断地缓冲震动，导致碳刷和集电环不断地被摩擦，这样极易因摩擦而导致磨损破坏，并且，其对温度也比较敏感，容易因温差变化而受到损坏，严重影响了转向电机的稳定性和寿命。
 技术问题
本发明的目的在于提供一种转向电机的减震机构，旨在解决现有技术中，传统转向电机的减震系统中存在，油缸组件内的部件之间因不断摩擦而导致结构磨损破坏，以及温差变化导致结构损坏，而影响转向电机的稳定性和使用寿命的缺陷。
 技术解决方案
本发明提供的技术方案是，一种转向电机的减震机构，设置于所述转向电机内，该减震机构包括上盖缓冲组件，置于所述上盖缓冲组件下方的分油盘，所述分油盘与所述上盖缓冲组件盖合形成密封的轴向型腔；所述分油盘下方固设有油缸组件，所述油缸组件包括两端开口的油缸，设于所述油缸中且上端具有开口的弹性油囊，所述弹性油囊的上端与所述油缸内壁固定连接，且连通所述轴向型腔，所述油缸内还设有沿所述油缸轴向滑动的活塞，所述活塞连接于所述弹性油囊下端。
优选地，所述上盖缓冲组件包括上盖和缓冲组件，所述缓冲组件包括依序层叠设置于所述轴向型腔内的弹性体、弹性隔环以及弹性隔膜，所述弹性隔膜的边缘嵌入所述上盖内侧下缘且与所述轴向型腔内壁紧固形成封闭。
进一步地，所述分油盘的下端中设有阻尼孔，所述阻尼孔正对于所述弹性油囊的上端布置，且分别连通所述轴向型腔及所述弹性油囊。
进一步地，所述阻尼孔的孔径小于所述弹性油囊上端开口的口径。
优选地，所述弹性隔膜呈蝶形状，所述分油盘通过紧固件与所述上盖缓冲组件盖合密封。
进一步地，所述分油盘中设有沿径向布置且与所述轴向型腔连通的过油通道，所述分油盘上设有进油口，所述分油盘中分别向上和向下延伸有沿轴向布置的具有内腔的中空柱，所述中空柱的内壁上开设有连通所述过油通道的过油口。
更进一步地，所述中空柱的内侧设有具有阀芯的换向阀，所述中空柱的内侧壁与所述换向阀的外壁形成第一径向型腔，所述第一径向型腔中嵌入有销钉，所述第一径向型腔被所述销钉隔离形成相互独立的分油盘进油型腔和分油盘出油型腔，所述分油盘进油型腔与所述进油口连通，所述分油盘出油型腔与所述轴向型腔连通；
所述阀腔侧壁上部开设有沿径向贯通布置的换向阀过油通道，所述换向阀过油通道轴向的下方开设有沿径向布置的过油孔；
所述阀芯上端的外壁上环设有截面呈半圆形的过油环槽，所述过油环槽连通所述分油盘进油型腔和所述分油盘出油型腔；
所述阀芯下端的外壁与所述阀腔下部侧壁形成第二径向型腔，所述阀腔下部开设有出油口，所述出油口与所述第二径向型腔连通。
进一步地，所述换向阀还包括置于所述分油盘下方且套设于所述阀腔外周的绕组线圈。
优选地，所述减震机构包括包括多个所述油缸组件，各所述油缸组件均置于所述分油盘下方，且于所述转向电机内呈圆周布置。
 有益效果
与现有技术相比，本发明提供的转向电机的减震机构，在油缸组件中采用了弹性油囊，并将弹性油囊与型腔密封连通，克服了传统液压减震系统中因摩擦导致构件损坏的问题，及对温度敏感的缺陷，延长了减震机构的使用寿命，节约了成本。
 附图说明
图1为本发明实施例提供的减震机构运用于转向电机的剖面示意图；
图2为图1的局部放大示意图；
图3为图1中分油盘部分的局部放大示意图；
图4为图1中换向阀部分的局部放大示意图；
图5为图1中A-A剖切方向的剖切示意图；
图6为图1中B-B剖切方向的剖切示意图。
 本发明的实施方式
为了使本发明的目的、技术方案及优点更加清楚明白，以下结合附图及实施例，对本发明进行进一步详细说明。应当理解，此处所描述的具体实施例仅仅用以解释本发明，并不用于限定本发明。
以下结合具体实施例对本发明的实现进行详细的描述。
如图1~6所示，为本发明提供的一个较佳实施例。
本实施例提供了一种转向电机的减震机构，其设置在转向电机的内部，该减震机构包括：上盖缓冲组件1、分油盘2和油缸组件5，其中，分油盘2设置在上盖缓冲组件1的下方，且上盖缓冲组件1和分油盘2盖合形成有密封的轴向型腔4，该轴向型腔4内设置有与油液配合用于缓冲震动的缓冲组件11；油缸组件5固定设置在分油盘2的下方，该油缸组件5包括油缸51、弹性油囊52和活塞53，油缸51的两端具有开口，弹性油囊52和活塞53均设置在该油缸51中，弹性油囊52为上端开口的囊状弹性隔膜，且弹性油囊52上端开口的边缘与油缸51上端开口的内壁固定连接，从而形成对油缸51上端开口的密封，并且，弹性油囊52上端的开口与轴向型腔4连通，另外，活塞53固定连接于弹性油囊52的下端，且该活塞53在油缸51中，可以沿油缸51的内腔轴向滑动。
当转向电机发生震动时，活塞53会随着转向电机的震动而在油缸51内上下滑动，通过其滑动而牵引弹性油囊52拉伸或者压缩，当弹性油囊52被压缩时，弹性油囊52内的油液会被挤压而流动到轴向型腔4内，接着油液压缩缓冲组件11而导致其发生弹性形变，进而实现缓冲震动，当弹性油囊52被拉伸时，轴向型腔4内的油液会回流至弹性油囊52中，缓冲组件11恢复形变。
采用上述的减震机构对转向电机进行缓冲减震，具有以下特点：
采用上盖缓冲组件1与分油盘2盖合形成了密封的轴向型腔4，在分油盘2下侧设置了与轴向型腔4对接的油缸组件5，通过油缸组件5中的弹性油囊52与轴向型腔4密封连通，弹性油囊52克服了传统液压减震机构的油缸组件5中部件易磨损，且对温度敏感的缺陷，延长了减震机构的使用寿命，也节约了成本。
本实施例中，上述上盖缓冲组件1包括上盖12和缓冲组件11，此处，设置缓冲组件11的目的是，通过其弹性形变而实现缓冲减震，该缓冲组件11包括弹性体111、弹性隔环112和弹性隔膜113，其中，弹性体111、弹性隔环112和弹性隔膜113自上而下依序层叠设置在上述轴向型腔4内，弹性隔膜113的边缘嵌入上盖12内侧下缘且与轴向型腔4的内壁固定连接并形成密封，这样，弹性体111和弹性隔环112就被弹性隔膜113密封在轴向型腔4内壁与弹性隔膜113形成的腔室内，此处，弹性体111和弹性隔环112可以在该腔室内活动，当然，在其他实施例中，根据实际情况和需要，缓冲组件11还可以为其他形式的缓冲结构。
上述分油盘2下端的底面中开设有阻尼孔26，该阻尼孔26正对于上述弹性油囊52上端的开口布置，这样，弹性油囊52通过该阻尼孔26与上述轴向型腔4构成连通，当然，在其他实施例中，弹性油囊52也可以通过其他的方式与上述轴向型腔4密封连通，比如管道连通，或者通道连通等。
并且，上述阻尼孔26的孔径小于弹性油囊52上端开口的口径，这样，当弹性油囊52受到上述活塞53压迫时，其内的油液被挤压而通过阻尼孔26进入上述轴向型腔4，该阻尼孔26也就起到了阻尼缓冲的作用，当然，这只是缓冲的一种形式，在其他实施例中，也可以采用其他的缓冲形式。
本实施例中，上述弹性隔膜113呈蝶形状，当然，上述分油盘2的结构与上盖缓冲组件1的结构相匹配对应，两者盖合并通过紧固件实现密封连接，当然，在其他实施例中，根据具体情况和实际需要，上述上盖缓冲组件1和上述分油盘2也可以为其他形式的结构。
为了配合转向电机外部的油液注入减震机构内，在上述分油盘2中设有中空柱21、进油口22和沿径向布置且连通上述轴向型腔4的过油通道23，中空柱21的内壁上开设有过油口，通过该过油口使得中空柱21内腔与过油通道23连通。
上述中空柱21的内侧设有换向阀3，换向阀3具有阀芯31和阀腔32；中空柱21的内壁与阀腔32外壁形成第一径向型腔，该第一径向型腔中嵌入有销钉6，第一径向型腔被销钉6隔离形成两个相互独立的径向型腔，其中一个为分油盘进油型腔24，该分油盘进油型腔24与进油口22连通。
为了对输入油液的通断进行控制，上述中空柱21内腔侧壁与阀腔32外壁配合形成的第一径向型腔，被嵌入其中的销钉6隔离形成的另一径向型腔，即为分油盘出油型腔25，该分油盘出油型腔25与轴向型腔4连通；在阀腔32侧壁上部开设有沿径向贯通布置的换向阀过油通道33，在换向阀过油通道33的轴向下方开设有沿径向布置的过油孔34；另外，阀芯31外壁的上部环设有截面呈半圆形的过油环槽35，该过油环槽35分别连通分油盘进油型腔24与分油盘出油型腔25；阀芯31下端的外壁与阀腔32下部内壁之间形成第二径向型腔36，阀腔32下部开设有出油口37，该出油口37与第二径向型腔36连通。
油液的进入路线是，由进油口22进入分油盘进油型腔24，穿过换向阀过油通道33与过油环槽35配合的油道，油液流经过分油盘出油型腔25，进入上述轴向型腔4内，接着穿过上述阻尼孔26进入上述弹性油囊52内。
通过换向阀阀芯31在其阀腔32内壁中上下移动，以及过油环槽35和多道O形密封圈38与阀腔32内壁的配合，实现了对过油孔34与第二径向型腔36的连通或者阻断，进而实现了分油盘进油型腔24与上述轴向型腔4的连通或者阻断。当然，在其他实施例中，根据实际情况和需求，也可采用其他的构件或者方式对过油通道中油液的通断进行控制。
本实施例中，上述的换向阀3采用的是电磁换向阀，该换向阀3还包括绕组线圈39；具体地，阀腔32设在中空柱21上部的内壁，绕组线圈39套设在阀腔32外壁，该外壁上设有轴向定位凸缘，绕组线圈39且位于中空柱21的下方和阀腔32外壁定位凸缘的上方。当然，在其他实施例中，根据实际情况和需要，也可以采用其他类型的换向阀。
初始状态下，过油环槽35与过油通道23错开，换向阀过油通道33被阀芯31的外壁所封堵，此时，第二径向型腔36通过过油孔34与分油盘进油型腔24连通，即分油盘进油型腔24与第二径向型腔36形成的油道构成通路，且分油盘进油型腔24与上述轴向型腔4以及弹性油囊52形成的油道被阻断；当绕组线圈39通电时，阀芯31整体下移，过油环槽35与过油通道33对准连通，阀芯31下部锥面的O型密封圈38压紧了阀腔32下部的圆锥面，即第二径向型腔36被封堵；这样，分油盘进油型腔24与轴向型腔4以及弹性油囊52形成的油道构成通路，同时，分油盘进油型腔24与第二径向型腔36形成的油道被阻断；通过换向阀3的换向切换作用实现了两条路道的切换，且互不干扰。
本实施例中，上述减震机构内设置了多组油缸组件5，各组油缸组件5全部设置在上述分油盘2的下方，各组油缸组件5的上端均与分油盘2的底面相抵接，自然地，各组油缸组件5中的各个弹性油囊52通过各个对应的阻尼孔26与上述轴向型腔4连通，另外，各组油缸组件5呈圆周布置于转向电机内部。当然，在其他实施例中，油缸组件5的数量可以根据具体情况而确定，并且，各组油缸组件5也可以呈其他形式分布。
上所述仅为本发明的较佳实施例而已，并不用以限制本发明，凡在本发明的精神和原则之内所作的任何修改、等同替换和改进等，均应包含在本发明的保护范围之内。

Claims (9)

  1. 一种转向电机的减震机构，设置于所述转向电机内，其特征在于，包括上盖缓冲组件，置于所述上盖缓冲组件下方的分油盘，所述分油盘与所述上盖缓冲组件盖合形成密封的轴向型腔；所述分油盘下方固设有油缸组件，所述油缸组件包括两端开口的油缸，设于所述油缸中且上端具有开口的弹性油囊，所述弹性油囊的上端与所述油缸内壁固定连接，且连通所述轴向型腔，所述油缸内还设有沿所述油缸轴向滑动的活塞，所述活塞连接于所述弹性油囊下端。
  2. 如权利要求1所述的转向电机的减震机构，其特征在于，所述上盖缓冲组件包括上盖和缓冲组件，所述缓冲组件包括依序层叠设置于所述轴向型腔内的弹性体、弹性隔环以及弹性隔膜，所述弹性隔膜的边缘嵌入所述上盖内侧下缘且与所述轴向型腔内壁紧固形成封闭。
  3. 如权利要求1所述的转向电机的减震机构，其特征在于，所述分油盘的下端中设有阻尼孔，所述阻尼孔正对于所述弹性油囊的上端布置，且分别连通所述轴向型腔及所述弹性油囊。
  4. 如权利要求3所述的转向电机的减震机构，其特征在于，所述阻尼孔的孔径小于所述弹性油囊上端开口的口径。
  5. 如权利要求2所述的转向电机的减震机构，其特征在于，所述弹性隔膜呈蝶形状，所述分油盘通过紧固件与所述上盖缓冲组件盖合密封。
  6. 如权利要求5所述的转向电机的减震机构，其特征在于，所述分油盘中设有沿径向布置且与所述轴向型腔连通的过油通道，所述分油盘上设有进油口，所述分油盘中分别向上和向下延伸有沿轴向布置的具有内腔的中空柱，所述中空柱的内壁上开设有连通所述过油通道的过油口。
  7. 如权利要求6所述的转向电机的减震机构，其特征在于，所述中空柱的内侧设有具有阀芯的换向阀，所述中空柱的内侧壁与所述换向阀的外壁形成第一径向型腔，所述第一径向型腔中嵌入有销钉，所述第一径向型腔被所述销钉隔离形成相互独立的分油盘进油型腔和分油盘出油型腔，所述分油盘进油型腔与所述进油口连通，所述分油盘出油型腔与所述轴向型腔连通；所述阀腔侧壁上部开设有沿径向贯通布置的换向阀过油通道，所述换向阀过油通道轴向的下方开设有沿径向布置的过油孔；所述阀芯上端的外壁上环设有截面呈半圆形的过油环槽，所述过油环槽连通所述分油盘进油型腔和所述分油盘出油型腔；所述阀芯下端的外壁与所述阀腔下部侧壁形成第二径向型腔，所述阀腔下部开设有出油口，所述出油口与所述第二径向型腔连通。
  8. 如权利要求7所述的转向电机的减震机构，其特征在于，所述换向阀还包括置于所述分油盘下方且套设于所述阀腔外周的绕组线圈。
  9. 如权利要求1~8任一项所述的转向电机的减震机构，其特征在于，包括多个所述油缸组件，各所述油缸组件均置于所述分油盘下方，且于所述转向电机内呈圆周布置。
PCT/CN2014/074346 2014-03-31 2014-03-31 一种转向电机的减震机构 Ceased WO2015149207A1 (zh)

Priority Applications (15)

Application Number Priority Date Filing Date Title
US15/300,534 US10348154B2 (en) 2014-03-31 2014-03-31 Shock absorption mechanism of steering motor
ES14888401T ES2794086T3 (es) 2014-03-31 2014-03-31 Mecanismo de absorción de impactos de un motor de dirección
JP2016559977A JP6386078B2 (ja) 2014-03-31 2014-03-31 ステアリングモータの衝撃吸収機構
KR1020167028554A KR102128148B1 (ko) 2014-03-31 2014-03-31 조향 모터의 댐핑 기구
PCT/CN2014/074346 WO2015149207A1 (zh) 2014-03-31 2014-03-31 一种转向电机的减震机构
EP14888401.8A EP3128652B1 (en) 2014-03-31 2014-03-31 Shock absorption mechanism of steering motor
CN201480076951.5A CN106104983B (zh) 2014-03-31 2014-03-31 一种转向电机的减震机构
EP14887872.1A EP3127778B1 (en) 2014-03-31 2014-04-02 Double oil passage structure of steering motor
US15/300,691 US10348155B2 (en) 2014-03-31 2014-04-02 Double oil passage structure of steering motor
KR1020167028405A KR102128146B1 (ko) 2014-03-31 2014-04-02 조향 모터의 이중 유도 구조
CN201480076947.9A CN106488868B (zh) 2014-03-31 2014-04-02 一种转向电机的双油道结构
JP2016559975A JP6386076B2 (ja) 2014-03-31 2014-04-02 ステアリングモータの双油路構造
PCT/CN2014/074600 WO2015149296A1 (zh) 2014-03-31 2014-04-02 一种转向电机的双油道结构
PL14887872T PL3127778T3 (pl) 2014-03-31 2014-04-02 Podwójna struktura kanałów olejowych silnika wspomagania układu kierowniczego
ES14887872T ES2750554T3 (es) 2014-03-31 2014-04-02 Estructura de doble paso de aceite del motor de dirección

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/CN2014/074346 WO2015149207A1 (zh) 2014-03-31 2014-03-31 一种转向电机的减震机构

Publications (1)

Publication Number Publication Date
WO2015149207A1 true WO2015149207A1 (zh) 2015-10-08

Family

ID=54239201

Family Applications (2)

Application Number Title Priority Date Filing Date
PCT/CN2014/074346 Ceased WO2015149207A1 (zh) 2014-03-31 2014-03-31 一种转向电机的减震机构
PCT/CN2014/074600 Ceased WO2015149296A1 (zh) 2014-03-31 2014-04-02 一种转向电机的双油道结构

Family Applications After (1)

Application Number Title Priority Date Filing Date
PCT/CN2014/074600 Ceased WO2015149296A1 (zh) 2014-03-31 2014-04-02 一种转向电机的双油道结构

Country Status (8)

Country Link
US (2) US10348154B2 (zh)
EP (2) EP3128652B1 (zh)
JP (2) JP6386078B2 (zh)
KR (2) KR102128148B1 (zh)
CN (2) CN106104983B (zh)
ES (2) ES2794086T3 (zh)
PL (1) PL3127778T3 (zh)
WO (2) WO2015149207A1 (zh)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN108916624A (zh) * 2018-08-14 2018-11-30 北京中冶华润科技发展有限公司 定量阀及定量喷射系统

Families Citing this family (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP6386077B2 (ja) * 2014-03-31 2018-09-05 深▲せん▼市智行単軸双輪駆動技術有限公司 ステアリングモーター
CN106233588B (zh) * 2014-03-31 2019-02-01 深圳市智行单轴双轮驱动技术有限公司 一种转向电机
CN106104983B (zh) * 2014-03-31 2018-08-17 深圳市智行单轴双轮驱动技术有限公司 一种转向电机的减震机构
CN106926899B (zh) * 2017-03-16 2018-09-07 合肥工业大学 一种抑制汽车转向轮多极限环自激摆振的减振装置
CN107975444B (zh) * 2018-01-15 2024-01-26 江苏龙擎动力科技股份有限公司 一种发电机组的独立油箱
CN108494153B (zh) * 2018-03-05 2019-10-15 浙江台州美多模具有限公司 一种振动幅度小的运行平稳的新能源汽车电机
CN109203401B (zh) * 2018-09-30 2024-03-01 广州市型腔模具制造有限公司 一种优化密集排布液压油缸连接油路的转接结构
CN109084164B (zh) * 2018-10-25 2024-03-22 绵阳富临精工机械股份有限公司 一种用于机油控制阀的阀套

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6144137A (en) * 1998-12-02 2000-11-07 Trw Inc. Electric motor assembly for a vehicle steering system
KR20020015420A (ko) * 2000-08-22 2002-02-28 밍 루 전동식 파워스티어링장치의 모터
JP2012080620A (ja) * 2010-09-30 2012-04-19 Nsk Ltd モータ及び電動パワーステアリング装置
CN103404005A (zh) * 2011-03-04 2013-11-20 三菱电机株式会社 电动机驱动装置

Family Cites Families (39)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB531099A (en) * 1939-07-07 1940-12-30 Ribbesford Company Ltd Improvements in or relating to telescopic shock absorbers
GB542142A (en) * 1940-06-24 1941-12-29 Automotive Prod Co Ltd Improvements in or relating to shock absorbers
US2589341A (en) * 1946-09-06 1952-03-18 Houdaille Hershey Corp Hydraulic steering motor and shimmy dampener
FR1076192A (fr) * 1953-02-13 1954-10-25 Blaw Knox Cie Fse Perfectionnements aux appareils à fluide tels que vérins, accumulateurs d'énergie, ou amortisseurs par exemple
US2944639A (en) * 1956-07-30 1960-07-12 William T Blake Shock absorber with vacuum compensator
JPS4819972B1 (zh) * 1968-09-17 1973-06-18
JPS557520U (zh) * 1978-06-28 1980-01-18
DE3231878C1 (de) * 1982-08-27 1983-11-24 Zahnradfabrik Friedrichshafen Ag, 7990 Friedrichshafen Pumpe fuer hydraulische Anlagen
DE3468386D1 (en) * 1983-11-05 1988-02-11 Zahnradfabrik Friedrichshafen Rack servo-steering, particularly for motor vehicles
US4598220A (en) * 1984-08-15 1986-07-01 Universal Electric Company End play and lubricating system for fractional horsepower electric motors
JPS6259166A (ja) * 1985-09-09 1987-03-14 Koyo Seiko Co Ltd 動力舵取装置に於ける操舵力制御装置
JPH0739272B2 (ja) * 1986-11-12 1995-05-01 いすゞ自動車株式会社 キヤブテイルト・サスペンシヨン装置
DE69406488T2 (de) * 1993-05-06 1998-03-19 Honeywell Inc Ein regelbarer Dämpfer und Isolator
US6293530B1 (en) * 1995-01-10 2001-09-25 Liquidspring Technologies, Inc. Compressible liquid vibration control system
JP3600274B2 (ja) * 1994-08-25 2004-12-15 倉敷化工株式会社 振動緩衝装置
US5961309A (en) * 1997-04-24 1999-10-05 Trw Inc. Gear pump with noise attenuation
JP4601764B2 (ja) * 2000-04-18 2010-12-22 株式会社ショーワ 可変容量型ポンプ
JP3773768B2 (ja) 2000-08-30 2006-05-10 株式会社ジェイテクト ダンパーバルブ及びそれを用いた油圧式パワーステアリング装置
EP1421666B1 (de) * 2001-08-30 2006-10-11 Siemens Aktiengesellschaft Schockfeste elektrische schiffsmaschine, z.b. motor oder generator
JP4716679B2 (ja) * 2003-06-25 2011-07-06 日本精工株式会社 ウォーム減速機及び電動式パワーステアリング装置
JP4760281B2 (ja) 2004-10-12 2011-08-31 日産自動車株式会社 制振装置、車両用電動機、および車両用駆動装置
CN2742662Y (zh) * 2004-11-12 2005-11-23 西北工业大学 一种带有螺旋冷却油路的电机转子轴
JP4615405B2 (ja) * 2004-11-22 2011-01-19 日立オートモティブシステムズ株式会社 モータ制御装置、パワーステアリング装置および制動力制御装置
CN200964129Y (zh) * 2006-10-26 2007-10-24 江门市兴江转向器有限公司 电控液压动力转向器总成
JP5448537B2 (ja) * 2008-09-03 2014-03-19 Ｎｔｎ株式会社 車両駆動用モータ
CN101635484B (zh) * 2009-08-24 2011-07-27 浙江大学 一种集成式液压驱动的永磁同步发电机
JP5365880B2 (ja) * 2010-06-08 2013-12-11 アイシン・エィ・ダブリュ株式会社 車両用駆動装置
JP5471955B2 (ja) * 2010-08-06 2014-04-16 アイシン・エィ・ダブリュ株式会社 回転電機及び車両用駆動装置
JP5278774B2 (ja) * 2010-08-06 2013-09-04 アイシン・エィ・ダブリュ株式会社 車両用駆動装置
CN102052324B (zh) * 2011-01-17 2012-05-30 浙江博阳压缩机有限公司 卧式旋转式中低温压缩机的油分离及回油润滑系统
JP2012245811A (ja) * 2011-05-25 2012-12-13 Nsk Ltd ラック・アンド・ピニオン式ステアリング装置
CN102638133B (zh) * 2012-03-23 2015-04-08 奇瑞汽车股份有限公司 一种永磁电机
JP6135982B2 (ja) * 2013-01-17 2017-05-31 日本電産株式会社 モータ
CN103291613B (zh) * 2013-06-14 2014-05-28 襄阳绿控电气科技有限公司 一种电动汽车用电动助力转向泵
CN106104983B (zh) * 2014-03-31 2018-08-17 深圳市智行单轴双轮驱动技术有限公司 一种转向电机的减震机构
CN106233588B (zh) * 2014-03-31 2019-02-01 深圳市智行单轴双轮驱动技术有限公司 一种转向电机
JP6386077B2 (ja) * 2014-03-31 2018-09-05 深▲せん▼市智行単軸双輪駆動技術有限公司 ステアリングモーター
JP6556261B2 (ja) * 2015-05-07 2019-08-07 ローベルト ボッシュ オートモーティブ ステアリング ゲゼルシャフト ミット ベシュレンクテル ハフツングＲｏｂｅｒｔ Ｂｏｓｃｈ Ａｕｔｏｍｏｔｉｖｅ Ｓｔｅｅｒｉｎｇ ＧｍｂＨ ステアリングシャフトを支持するための軸受ユニット
KR102613788B1 (ko) * 2016-10-25 2023-12-15 에이치엘만도 주식회사 자동차 조향장치

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6144137A (en) * 1998-12-02 2000-11-07 Trw Inc. Electric motor assembly for a vehicle steering system
KR20020015420A (ko) * 2000-08-22 2002-02-28 밍 루 전동식 파워스티어링장치의 모터
JP2012080620A (ja) * 2010-09-30 2012-04-19 Nsk Ltd モータ及び電動パワーステアリング装置
CN103404005A (zh) * 2011-03-04 2013-11-20 三菱电机株式会社 电动机驱动装置

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See also references of EP3128652A4 *

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN108916624A (zh) * 2018-08-14 2018-11-30 北京中冶华润科技发展有限公司 定量阀及定量喷射系统

Also Published As

Publication number Publication date
EP3128652A1 (en) 2017-02-08
JP6386076B2 (ja) 2018-09-05
ES2794086T3 (es) 2020-11-17
WO2015149296A1 (zh) 2015-10-08
US20170110927A1 (en) 2017-04-20
KR102128148B1 (ko) 2020-06-30
EP3127778A4 (en) 2017-11-22
JP6386078B2 (ja) 2018-09-05
ES2750554T3 (es) 2020-03-26
EP3128652B1 (en) 2020-03-04
US20170110931A1 (en) 2017-04-20
US10348155B2 (en) 2019-07-09
CN106104983A (zh) 2016-11-09
KR20160140730A (ko) 2016-12-07
US10348154B2 (en) 2019-07-09
CN106488868A (zh) 2017-03-08
EP3127778B1 (en) 2019-07-24
CN106104983B (zh) 2018-08-17
EP3127778A1 (en) 2017-02-08
KR20160138116A (ko) 2016-12-02
JP2017511276A (ja) 2017-04-20
JP2017511277A (ja) 2017-04-20
EP3128652A4 (en) 2018-01-24
PL3127778T3 (pl) 2019-12-31
CN106488868B (zh) 2019-06-21
KR102128146B1 (ko) 2020-06-30

Similar Documents

Publication Publication Date Title
WO2015149207A1 (zh) 一种转向电机的减震机构
WO2015149209A1 (zh) 一种转向电机
US4696379A (en) Hydraulic buffer
WO2015149208A1 (zh) 一种转向电机
CN100348446C (zh) 电磁致动阀
CN101886641A (zh) 一种平衡阀
CN102032309A (zh) 一种容积可变的空气弹簧附加气室
CN201891791U (zh) 一种容积可变的空气弹簧附加气室
CN113969913A (zh) 一种高频大流量电液伺服阀
CN202418647U (zh) 一种双级平衡式软硬密封最小流量阀
CN205800078U (zh) 一种用于针阀式热流道系统的阀针控制装置
CN219623318U (zh) 一种内置式二位五通双控换向阀
CN103625457B (zh) 单向调压阀
CN205841608U (zh) 一种汽车动力总成主动控制式液压悬置
CN117365709A (zh) 一种自封滑油滤
CN209340397U (zh) 一种基于共振方式的频率敏感阻尼油气弹簧
CN102943897B (zh) 气动膜片式压差自动换向阀
EP3690293B1 (en) Block and fluid control device
CN103661587B (zh) 一种车辆转向防偏摆阀
CN219953798U (zh) 一种车桥扩展油缸
CN114876999B (zh) 多容腔高可靠性油气弹簧
CN116517912B (zh) 液压油缸
CN110905962B (zh) 一种带有环形减振阀的油气弹簧
CN224017612U (zh) 分体式双腔空气弹簧及车用减震器
CN211550619U (zh) 一种阀安装座及膜片式控制阀

Legal Events

Date Code Title Description
121 Ep: the epo has been informed by wipo that ep was designated in this application

Ref document number: 14888401

Country of ref document: EP

Kind code of ref document: A1

ENP Entry into the national phase

Ref document number: 2016559977

Country of ref document: JP

Kind code of ref document: A

WWE Wipo information: entry into national phase

Ref document number: 15300534

Country of ref document: US

NENP Non-entry into the national phase

Ref country code: DE

REEP Request for entry into the european phase

Ref document number: 2014888401

Country of ref document: EP

WWE Wipo information: entry into national phase

Ref document number: 2014888401

Country of ref document: EP

ENP Entry into the national phase

Ref document number: 20167028554

Country of ref document: KR

Kind code of ref document: A