WO2015188650A1 - 铰接内杆式流体传动缸 - Google Patents

铰接内杆式流体传动缸 Download PDF

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Publication number
WO2015188650A1
WO2015188650A1 PCT/CN2015/075527 CN2015075527W WO2015188650A1 WO 2015188650 A1 WO2015188650 A1 WO 2015188650A1 CN 2015075527 W CN2015075527 W CN 2015075527W WO 2015188650 A1 WO2015188650 A1 WO 2015188650A1
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WO
WIPO (PCT)
Prior art keywords
rod
plunger
cylinder
hinged
acting
Prior art date
Application number
PCT/CN2015/075527
Other languages
English (en)
French (fr)
Inventor
吴建友
窦云霞
钟康民
Original Assignee
苏州劳灵精密机械有限公司
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
Priority claimed from CN201410259366.0A external-priority patent/CN103994119A/zh
Priority claimed from CN201410261792.8A external-priority patent/CN104006025B/zh
Application filed by 苏州劳灵精密机械有限公司 filed Critical 苏州劳灵精密机械有限公司
Priority to DE112015002779.3T priority Critical patent/DE112015002779T5/de
Publication of WO2015188650A1 publication Critical patent/WO2015188650A1/zh

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B15/00—Fluid-actuated devices for displacing a member from one position to another; Gearing associated therewith
    • F15B15/08—Characterised by the construction of the motor unit
    • F15B15/14—Characterised by the construction of the motor unit of the straight-cylinder type
    • F15B15/1423—Component parts; Constructional details
    • F15B15/1466—Hollow piston sliding over a stationary rod inside the cylinder
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B15/00—Fluid-actuated devices for displacing a member from one position to another; Gearing associated therewith
    • F15B15/02—Mechanical layout characterised by the means for converting the movement of the fluid-actuated element into movement of the finally-operated member
    • F15B15/04—Mechanical layout characterised by the means for converting the movement of the fluid-actuated element into movement of the finally-operated member with oscillating cylinder
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B15/00—Fluid-actuated devices for displacing a member from one position to another; Gearing associated therewith
    • F15B15/08—Characterised by the construction of the motor unit
    • F15B15/14—Characterised by the construction of the motor unit of the straight-cylinder type
    • F15B15/1423—Component parts; Constructional details
    • F15B15/1447—Pistons; Piston to piston rod assemblies
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B15/00—Fluid-actuated devices for displacing a member from one position to another; Gearing associated therewith
    • F15B15/08—Characterised by the construction of the motor unit
    • F15B15/14—Characterised by the construction of the motor unit of the straight-cylinder type
    • F15B15/1423—Component parts; Constructional details
    • F15B15/1457—Piston rods
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/705—Output members, e.g. hydraulic motors or cylinders or control therefor characterised by the type of output members or actuators
    • F15B2211/7051—Linear output members
    • F15B2211/7052—Single-acting output members

Definitions

  • the invention relates to a hinged inner rod type fluid transmission cylinder, namely a hydraulic cylinder or a cylinder.
  • Plunger-type hydraulic cylinders or cylinders have lower manufacturing costs than piston-type hydraulic cylinders or cylinders because there is no front end cover and corresponding sealing device.
  • the plunger cylinders are single-acting, that is, the return stroke of the plunger needs to be achieved by an external force such as gravity, return spring force, and the like.
  • small and medium-sized hydraulic cylinders or cylinders are mostly reset by providing a spring outside the cylinder, resulting in a large overall structural size.
  • Chinese Patent Application Publication No. 102979781A proposes a plunger cylinder in which a return tension spring is disposed in a bore of a plunger. The structure of the plunger cylinder is as shown in FIG.
  • the advantage of this type of plunger cylinder is that it reduces the overall structural size significantly, but it also has the following significant disadvantages: (1) Due to the use of a tension spring, it is necessary to provide a spring hook in the inner bore of the plunger and on the rear end cap. The device not only causes poor processingmanship of the relevant parts, but also the assembly of the spring is extremely inconvenient; (2) due to the tension spring used, the mechanical properties are linear, that is, the restoring force of the spring is proportional to the amount of deformation, Therefore, there is a large difference between the minimum resetting force of the spring and the maximum resetting force, thereby causing unnecessary waste of force and correspondingly reducing the mechanical efficiency of the cylinder.
  • the conventional plunger cylinder and the plunger cylinder shown in Fig. 1 can only output reciprocating linear motion, and cannot output non-linear motion such as reciprocating swing.
  • a nonlinear motion such as a reciprocating swing
  • the disadvantage of this method is that the size of the whole device in the axial direction of the hydraulic cylinder or pneumatic cylinder is too large, very compact; the other is the rear end An articulated hydraulic or pneumatic cylinder, as shown in Fig.
  • the innovative design of a spring-return type plunger cylinder capable of outputting non-linear motion such as reciprocating oscillation, and having good manufacturing process and high force transmission efficiency can not only significantly expand the application field of the plunger cylinder, but also reduce the plunger.
  • the production cost of the cylinder and the reduction of the overall structural size have very positive and realistic significance.
  • An object of the present invention is to provide a hinged inner rod type hydraulic cylinder or cylinder which is capable of outputting a non-linear motion such as a reciprocating swing and having a high manufacturing processability and high force transmission efficiency.
  • an aspect of the present invention provides a single-acting hinged inner rod type plunger cylinder including a cylinder body, a rear end cover and a plunger, wherein the plunger is provided with an inner hole, and the inner hole is bored a guide rod assembly including a rod body and a large diameter end fixedly disposed at a front end of the rod body, a rear end of the rod body fixedly coupled to the rear end cover, the large diameter end
  • a guide rod assembly including a rod body and a large diameter end fixedly disposed at a front end of the rod body, a rear end of the rod body fixedly coupled to the rear end cover, the large diameter end
  • An inner space is formed in the inner hole relative to the plunger, an annular space is formed between a rear end of the plunger and the large diameter end, and a compression spring is disposed in the annular space, and the inner hole is
  • a hinged seat is fixedly disposed in the front of the large-diameter end in the inner hole, and a swinging rod is
  • the front end of the inner hole has a conical shape.
  • the compression spring is a nonlinear butterfly spring.
  • the hinge seat is in sealing contact with the circumferential side wall of the inner bore in the inner bore.
  • the rear end of the swinging lever is hinged to the hinge mount by a pin.
  • a rear end of the plunger is provided with a through hole through which the rod body passes, and an annular space is formed between a rear end inner side wall of the plunger and the large diameter end.
  • the inner hole of the plunger penetrates the plunger in a front-rear direction, and a rear end of the inner hole is fixedly provided with a cover, and a gap between the cover and the large-diameter end is formed Said annular space.
  • the large diameter end is integrally provided with the rod body, or the large diameter end is fixedly connected to the rod body.
  • a hinged inner rod double-acting cylinder comprising a cylinder body, a rear end cover, a front end cover and a piston rod, wherein the piston rod is provided with an inner hole, and the inner hole is fixedly disposed a hinge seat, the front end of the hinge seat is hinged with a swinging rod.
  • the front end of the inner hole on the piston rod has a conical shape.
  • the inner hole is a through hole
  • the hinge seat is sealingly connected with the circumferential side wall of the inner hole.
  • the front end of the swinging rod passes out of the outer side of the inner bore.
  • the rear end pin of the swinging lever is hinged on the hinged seat.
  • the rear end ball of the swinging lever is hinged on the hinge seat.
  • the plunger cylinder according to the present invention has the following advantages over the prior art:
  • the swinging lever is hinged on the plunger, so that the plunger cylinder can output the swinging motion, which solves the defect that the conventional plunger cylinder can only output the reciprocating linear motion, and the plunger cylinder can output non-linear motion such as reciprocating swing.
  • the swinging rod is balanced on the plunger when the swinging force is output, and the mechanical property is good;
  • the compression spring is disposed in the inner hole of the plunger, which significantly reduces the overall structural size of the plunger cylinder compared to the conventional plunger cylinder in which the return spring is disposed outside the cylinder;
  • the compression spring is used as the return spring, and the range of variation of the resetting force is small, which correspondingly improves the mechanical efficiency of the plunger cylinder, so that the force transmission efficiency of the plunger cylinder is improved, which is beneficial to energy saving;
  • the plunger cylinder has fewer components, and has good manufacturing and assembly processability and low production cost.
  • the conventional hydraulic pressure is solved compared with the conventional hydraulic cylinder and the cylinder, since the inner hole is opened in the piston rod and the swing rod is hinged to the hinge seat in the inner hole.
  • the cylinder and the cylinder can only output the defect of reciprocating linear motion, and the articulated inner rod cylinder can output non-linear motion such as reciprocating swing.
  • the axial connecting rod greatly reduces the axial dimension; compared with the rear-end articulated hydraulic cylinder or cylinder, the quality of the oscillating portion is greatly reduced, thereby Significantly reduce the negative impact of the impact.
  • Figure 1 is a schematic view showing the structure of a plunger cylinder in the prior art
  • FIG. 2 is a schematic structural view of a hydraulic cylinder or a pneumatic cylinder in which a front end of a piston rod is hinged with a strut;
  • Figure 3 is a schematic structural view of a rear end articulated hydraulic or pneumatic cylinder in the prior art
  • Figure 4 is a schematic view of the working principle of the plunger cylinder of Embodiment 1 of the present invention.
  • Figure 5 is a second schematic view showing the working principle of the plunger cylinder of Embodiment 1 of the present invention.
  • Figure 6 is a schematic view of the working principle of the plunger cylinder of Embodiment 2 of the present invention.
  • Figure 7 is a second schematic view of the working principle of the plunger cylinder of Embodiment 2 of the present invention.
  • Figure 8 is a schematic view of the working principle of the double-acting cylinder of the present invention.
  • Figure 9 is a second schematic view of the working principle of the double-acting cylinder of the present invention.
  • Figure 10 is a third schematic view of the working principle of the double-acting cylinder of the present invention.
  • the following definitions of the directions are defined according to the direction of the plunger movement when the plunger cylinder is in operation, and the direction in which the plunger moves outward relative to the cylinder is the front, and vice versa, that is, in FIGS. 4 to 10.
  • the cylinder block 1 and the rear end cover 3 fixedly disposed at the rear of the cylinder block 1 are disposed in the cylinder block 1 so as to be movable in the front-rear direction.
  • Plunger 2 An inner hole 21 is defined in the plunger 2, and the inner hole 21 is provided with a guide rod assembly 4 including a rod body 41 and a large diameter end 42 fixed to the front end of the rod body 41. The rear end of the rod body 41 is fixed. Connected to the rear end cover 3, the large diameter end 42 is movably disposed in the inner bore 21 with respect to the plunger 2.
  • the large-diameter end 42 may be integrally provided with the rod body 41, or may be separately processed and fixedly connected.
  • the inner hole 21 of the plunger 2 penetrates the plunger 2 in the front-rear direction, and the rear end of the inner hole 21 is fixedly provided with a cover 22, and an annular space is formed between the cover 22 and the large-diameter end 42 of the inner hole 21, the ring A compression spring 5 is provided in the space.
  • a hinge support 6 is also fixedly disposed in the inner hole 21, and the hinge support 6 is located in front of the large-diameter end 42 in the inner hole 21, and the hinge support 6 is in the inner hole 21 and the circumferential side of the inner hole 21.
  • the wall sealing connection is arranged such that a rear pressure chamber is formed between the rear end of the plunger cylinder, ie the rear end cover 3 and the hinge seat 6. At the time of installation, the hinge holder 6 can be fitted into the inner hole 21 by an interference fit.
  • the front end of the hinged seat 6 is hinged with a swinging rod 7, and the rear end of the swinging rod 7 can be hinged to the hinged seat 6 via a pin shaft, and can also be hinged to the hinged seat 6 by means of a ball joint.
  • the front end of the inner hole 21 is provided in a conical shape, which is an arrangement in which the rearward and forward apertures are gradually increased to give way to the swing of the swinging lever 7.
  • the front end of the swing lever 7 is connected to the output rod group 9 for power output.
  • the output rod set 9 includes a first rod 91, a second rod 92, and a punch 93.
  • One end of the first rod 91 is hinged to the frame, the other end of which is hinged at the front end of the swinging rod 7, one end of the second rod 92 is hinged at the front end of the swinging rod 7, and the other end is hinged to the punch 93, the punch 93 It can be mounted on the rack in a vertical direction.
  • the solenoid valve 8 operates such that the compressed gas/hydraulic oil enters the pressure chamber through the intake/oil inlet opening formed in the rear end cover 3, and the plunger 2 moves forward, causing the swing rod 7 to swing and act on The first rod 91 and the second rod 92 drive the first rod 91 and the second rod 92 to swing and drive the punch 93 to move downward to achieve an impact.
  • the compression spring 5 is pressed between the shutter 22 and the large diameter end 42.
  • the compression spring 5 employs a non-linear butterfly spring that is sleeved on the rod 41 in the annular space and between the shutter 22 and the large diameter end 42. Since the mechanical properties of the butterfly spring are nonlinear, when the butterfly spring is selected, a reasonable mechanical characteristic interval can be selected according to the working conditions of the actual application, so that the variation range of the spring restoring force can be greatly reduced, and the column can be effectively improved.
  • the mechanical efficiency of the plug cylinder is conducive to energy saving.
  • the traditional tension coil spring is linear because its mechanical characteristics are linear, and its stiffness is proportional to its deformation. When the deformation amount is large, the restoring force is significantly increased, and this resetting force needs to be additionally supplied to the plunger.
  • the force is overcome, and it is bound to cause the cylinder bore to expand under the condition that the system pressure is constant.
  • the present invention solves this problem well, and the diameter of the cylinder body is further reduced compared with the prior art.
  • the butterfly spring may be in the form of a lamination to increase the rigidity, which allows the output force of the plunger cylinder of the present invention to have a larger adjustment range, making it more versatile.
  • this embodiment differs from Embodiment 1 only in the arrangement of the plunger 2.
  • the rear end of the plunger 2 is open for the rod body 41 to penetrate and the large diameter end 42 cannot penetrate.
  • a through hole 23 is formed in the inner hole 21 between the large diameter end 42 and the inner side wall of the rear end of the plunger 2 to form an annular space for arranging the compression spring 5.
  • the working principle of the plunger cylinder is the same as that of the first embodiment.
  • the single-acting hinged inner rod type plunger cylinder of the present invention solves the defect that the conventional plunger cylinder can only output reciprocating linear motion compared with the conventional plunger cylinder, because the swing rod 7 is hinged on the plunger 2. It is capable of outputting a non-linear motion such as a reciprocating swing, and during the swinging force of the swinging lever 7, the plunger 2 is balanced in force and has good mechanical properties.
  • the compression spring is provided in the inner bore of the plunger 2, this significantly reduces the overall structural size of the plunger cylinder compared to the plunger cylinder in which the return spring is disposed outside the cylinder.
  • the mechanical characteristics of the plunger cylinder are non-linear due to the use of the compression spring, the range of variation of the restoring force is small, and the mechanical efficiency of the plunger cylinder is correspondingly increased, so that the force transmission of the plunger cylinder is achieved. Efficiency is improved and it is conducive to energy conservation.
  • the plunger cylinder component of the invention is small, and the manufacturing and assembly processability is good, and the production cost is low.
  • the double-acting cylinder shown in FIG. 8 to FIG. 10 may be a hydraulic cylinder or a cylinder, which includes a cylinder block 1, a rear end cover 3 fixed to the rear end of the cylinder block 1, and a front end cover 301 fixed to the front end of the cylinder block 1. And a piston rod 201 disposed in the cylinder block 1, the piston rod 201 separating the inner cavity of the cylinder block 1 into a separate left and right pressure chambers.
  • the rear end cover 3 is provided with a first oil hole/intake hole 31 communicating with the left pressure chamber
  • the front end cover 301 is provided with a second oil hole/intake hole 3011 communicating with the right pressure chamber, which is controlled by the electromagnetic valve 8.
  • Supplying or supplying air to the left pressure chamber or the right pressure chamber can drive the piston rod 201 to move back and forth relative to the cylinder block 1.
  • the piston rod 201 is provided with an inner hole 21, and the inner hole is fixedly provided with a hinge seat 6, wherein the inner hole 21 is provided as a through hole penetrating the piston rod 201 in the front-rear direction, and the hinge seat 6 and the inner hole 21 are The circumferential side wall sealing connection is provided, and the hinged seat 6 can be disposed in the inner hole 21 by an interference fit during installation.
  • the front end of the hinged seat 6 is hinged with a swinging lever 7, and the rear end of the swinging lever 7 can be hinged to the hinged seat 6 via a pin or hinged to the hinged seat 6 in a hinged manner.
  • the front end of the inner hole 21 is provided in a conical shape, which is an arrangement in which the rearward and forward apertures are gradually increased to give way to the swing of the swinging lever 7.
  • the front end of the swinging lever 7 is located outside the inner hole 21, and the front end of the swinging lever 7 is connected to the output rod group 9 for power output.
  • the output rod set 9 includes a first rod 91, a second rod 92, and a punch 93.
  • One end of the first rod 91 is hinged to the frame, the other end of which is hinged at the front end of the swinging rod 7, one end of the second rod 92 is hinged at the front end of the swinging rod 7, and the other end is hinged to the punch 93, the punch 93 It can be mounted on the rack in a vertical direction.
  • the piston rod 201 In the initial state, as shown in FIG. 8, the piston rod 201 is located at the rear of the cylinder 1.
  • the solenoid valve 8 When the piston rod 201 is required to move forward, as shown in FIG. 9, the solenoid valve 8 is reversed, the left pressure chamber is injected with hydraulic oil or filled with compressed gas, and the hydraulic oil in the right pressure chamber is gradually returned to the oil tank or the compressed gas is introduced into the air.
  • the piston rod 201 moves forward, the piston rod 201 acts on the swing rod 7 when it moves forward, and the swing rod 7 swings in the inner hole 21 and acts on the first rod 91 and the second rod 92 to drive the first rod 91 and
  • the second rod 92 swings and drives the punch 93 to move downward to achieve an impact, as shown in FIG.
  • the swing lever 7 can output a reciprocating swing or other non-linear motion according to the needs of the mechanism to which it is connected.
  • the conventional hydraulic cylinder and the cylinder are solved by the fact that the piston rod opens the inner hole and the swing rod is hinged to the hinge seat in the inner hole.
  • the hydraulic cylinder and the cylinder can only output the defect of reciprocating linear motion, and the articulated inner rod cylinder can output non-linear motion such as reciprocating swing.
  • the axial connecting rod greatly reduces the axial dimension; compared with the rear-end articulated hydraulic cylinder or cylinder, the quality of the oscillating portion is greatly reduced, thereby Significantly reduce the negative impact of the impact.

Abstract

公开了一种铰接内杆式流体传动缸，为液压缸或气缸，有单作用和双作用两种方式，包括缸体（1）、后端盖（3）、前端盖（301）和活塞杆（201）。活塞杆（201）上设有内孔（21），内孔（21）中固定地设有铰支座（6），铰支座（6）的前端铰接有摆动杆（7）。该铰接内杆式缸能够输出往复摆动等非直线运动，并且轴向尺寸大大缩小，摆动部分质量大幅降低，从而大幅地降低冲击所带来的负面影响。

Description

铰接内杆式流体传动缸
技术领域
本发明涉及一种铰接内杆式流体传动缸，即液压缸或气缸。
背景技术
柱塞式液压缸或气缸，相对于活塞式液压缸或气缸，由于不存在前端盖及相应密封装置，因而制造成本较低。但是，柱塞缸都是单作用式的，即柱塞的回程需要借助外力来实现，如重力、复位弹簧力等。其中，中小型的液压缸或气缸大多借助在缸体外设置弹簧来进行复位，造成总体结构尺寸较大。公开号为102979781A的中国发明专利申请，提出了一种在柱塞内孔中设置复位拉力弹簧的柱塞缸。该柱塞缸的结构如图1所示。这种柱塞缸的优点是显著减小了总体结构尺寸，但也具有以下显著缺点：（1）由于采用拉伸弹簧，所以必须在柱塞内孔中及后端盖上设置弹簧的钩挂装置，不仅造成相关零件的加工工艺性不好，而且弹簧的装配极为不便；（2）由于所采用的拉伸弹簧，其力学特性是线性的，亦即弹簧的复位力与其变形量成正比，所以，弹簧的最小复位力与最大复位力存在较大的差值，从而造成不必要的力浪费，相应降低了缸的机械效率。
此外，传统的柱塞缸与图1所示柱塞缸，都只能够输出往复直线运动，而不能够输出往复摆动等非直线运动。当需要输出往复摆动等非线性运动时，参照现有技术中的液压缸或气压缸中的设置方式，其通常采用两种方法，一种是在活塞杆12’的前端铰上一根支杆13’，以解决自由度不足的问题，如图2所示，这种方法的缺点是整个装置在液压缸或气压缸轴向上的尺寸过大，极不紧凑；另一种是采用后端铰接式的液压缸或气压缸，如图3所示，这种方法的缺点是缸体21’、活塞23’与活塞杆22’一起摆动，摆动部分的质量过大，造成惯性力很大，从而形成很大的冲击，整个装置的受力状态恶劣，冲击噪声也较大。
因此，创新设计出一种能够输出往复摆动等非直线运动的、制造工艺性好且力传递效率高的弹簧复位式柱塞缸，不仅能够显著扩大柱塞缸的应用领域，而且对降低柱塞缸的生产成本及缩小总体结构尺寸都具有非常积极而现实的意义。
发明内容
本发明的目的是提供一种能够输出往复摆动等非直线运动的、制造工艺性好且力传递效率高的铰接内杆式液压缸或气缸。
为达到上述目的，本发明一方面提供一种单作用铰接内杆式柱塞缸，包括缸体、后端盖和柱塞，所述柱塞中开设有内孔，所述内孔中穿设有导杆组件，所述导杆组件包括杆体和固定地设于所述杆体前端的大直径端头，所述杆体的后端固定地连接在所述后端盖上，所述大直径端头可相对所述柱塞移动地设于所述内孔中，所述柱塞的后端与所述大直径端头之间形成环形空间，所述环形空间内设有压缩弹簧，所述内孔中固定地设有铰支座，所述铰支座在所述内孔中位于所述大直径端头的前方，所述铰支座的前端铰接有摆动杆。
优选地，所述内孔的前端呈圆锥状。
优选地，所述压缩弹簧为非线性蝶形弹簧。
优选地，所述铰支座在所述内孔中与所述内孔的周向侧壁密封接触。
优选地，所述摆动杆的后端通过销轴铰接在所述铰支座上。
优选地，所述柱塞的后端开设有可供所述杆体穿过的通孔，所述柱塞的后端内侧壁与所述大直径端头之间形成所述环形空间。
优选地，所述柱塞上所述内孔沿前后方向贯穿所述柱塞，所述内孔的后端固定地设有挡盖，所述挡盖与所述大直径端头之间形成所述环形空间。
优选地，所述大直径端头与所述杆体一体设置，或者所述大直径端头与所述杆体固定连接设置。
本发明另一方面还提供一种铰接内杆式双作用缸，包括缸体、后端盖、前端盖、活塞杆，所述活塞杆上开设有内孔，所述内孔中固定地设有铰支座，所述铰支座的前端铰接有摆动杆。
优选地，所述活塞杆上所述内孔的前端呈圆锥状。
优选地，所述内孔为通孔，所述铰支座与所述内孔的周向侧壁密封连接设置。
优选地，所述摆动杆的前端穿出所述内孔外侧。
优选地，所述摆动杆的后端销铰在所述铰支座上。
优选地，所述摆动杆的后端球铰在所述铰支座上。
由于上述技术方案的运用，根据本发明的柱塞缸与现有技术相比具有下列优点：
（1）在柱塞上铰接摆动杆，使得该柱塞缸可输出摆动运动，解决了传统的柱塞缸只能输出往复直线运动的缺陷，该柱塞缸可输出往复摆动等非直线运动。且摆动杆在输出摆动力时柱塞上受力均衡，力学特性良好；
（2）将压缩弹簧设于柱塞的内孔中，这相比传统的在缸体外设置复位弹簧的柱塞缸，显著地减小了柱塞缸的整体结构尺寸；
（3）采用压缩弹簧作为复位弹簧，其复位力的变化范围幅度小，这相应地提高了柱塞缸的机械效率，使得该柱塞缸的力传递效率得到了提高，有利于节能；
（4）该柱塞缸部件较少，且制造和装配工艺性好，生产成本低。
根据本发明的铰接内杆式液压缸或气缸，相比传统的液压缸与气缸，由于活塞杆上开设内孔，并将摆动杆铰接在内孔中的铰支座上，解决了传统的液压缸与气缸仅能输出往复直线运动的缺陷，该铰接内杆式缸能够输出往复摆动等非直线运动。这相比传统的固定式液压缸与气缸的活塞杆的前端铰接连杆的方式，极大地缩小了轴向尺寸；而相比后端铰接式的液压缸或气缸，摆动部分质量大幅降低，从而大幅度地降低冲击所带来的负面影响。
附图说明
附图1为现有技术中柱塞缸的结构示意图；
附图2为现有技术中活塞杆前端铰接有支杆的液压缸或气压缸的结构示意图；
附图3为现有技术中后端铰接式的液压缸或气压缸的结构示意图；
附图4为本发明的实施例1的柱塞缸的工作原理示意图一；
附图5为本发明的实施例1的柱塞缸的工作原理示意图二；
附图6为本发明的实施例2的柱塞缸的工作原理示意图一；
附图7为本发明的实施例2的柱塞缸的工作原理示意图二；
附图8为本发明的双作用缸的工作原理示意图一；
附图9为本发明的双作用缸的工作原理示意图二；
附图10为本发明的双作用缸的工作原理示意图三。
其中：11’，21’ 缸体；12’，22’ 活塞杆； 13’、支杆；23’、活塞。
1、缸体；2、柱塞；21、内孔；22、挡盖；23、通孔；3、后端盖；4、导杆组件；41、杆体；42、大直径端头；5、压缩弹簧；6、铰支座；7、摆动杆；8、电磁换向阀；9、输出杆组；91、第一杆；92、第二杆；93、冲头;
3、后端盖；31、第一注油孔/进气孔；301、前端盖；3011、第二注油孔/进气孔；201、活塞杆。
具体实施方式
下面结合附图和具体的实施例来对本发明的技术方案作进一步的阐述。
以下关于方向的定义中，均是按照该柱塞缸工作时柱塞运动的方向来定义的，柱塞相对缸体向外移动的方向为前，反之为后，亦即图4至图10中的左右方向，其中左方为后，右方为前。
实施例1
参见图4、图5所示的单作用铰接内杆式柱塞缸，包括缸体1、固定设于缸体1后部的后端盖3、可沿前后方向移动地设于缸体1中的柱塞2。柱塞2中开设有内孔21，该内孔21中穿设有导杆组件4，该导杆组件4包括杆体41和固定在杆体41前端的大直径端头42，杆体41的后端固定地连接在后端盖3上，大直径端头42可相对柱塞2移动地设于内孔21中。在设置时导杆组件4，大直径端头42可与杆体41一体设置，也可以分开加工再将两者固定连接起来。
柱塞2上内孔21沿前后方向贯穿柱塞2，内孔21的后端固定地设有挡盖22，内孔21中挡盖22与大直径端头42之间形成环形空间，该环形空间内设有压缩弹簧5。
内孔21中还固定地设有铰支座6，该铰支座6在内孔21中位于大直径端头42的前方，铰支座6在内孔21中与内孔21的周向侧壁密封连接设置，从而使得该柱塞缸的后部，即后端盖3与铰支座6之间形成封闭的压力腔。在安装时，可通过过盈配合将铰支座6安装至内孔21中。
铰支座6的前端铰接有摆动杆7，摆杆7的后端可通过销轴铰接在铰支座6上，也可采用球头铰接的方式铰接在铰支座6上。内孔21的前端呈圆锥状设置，该圆锥状为由后向前孔径逐渐增大的设置，以对摆动杆7的摆动进行让位。摆动杆7的前端则连接用于动力输出的输出杆组9。在本实施例中，该输出杆组9包括第一杆91、第二杆92、冲头93。第一杆91的一端铰接在机架上，其另一端铰接在摆动杆7的前端，第二杆92的一端铰接在摆动杆7的前端，其另一端铰接在冲头93上，冲头93可沿竖直方向升降地设于机架上。
参见图4所示，在初始状态下，在压缩弹簧5的推力作用下，柱塞2的后端位于缸体1的后部。工作时，电磁阀8工作，使得压缩气体/液压油通过开设在后端盖3上的进气孔/进油孔进入压力腔中，柱塞2向前移动，带动摆动杆7摆动并作用于第一杆91与第二杆92，带动第一杆91和第二杆92摆动并驱动冲头93向下移动实现冲击。此时压缩弹簧5被挤压在挡盖22与大直径端头42之间。
当柱塞2向前运动结束后，电磁阀8换向，压力腔中的压缩气体通入大气或液压油回流至油箱，在压缩弹簧5的推力作用下，推动柱塞2向后移动，如图5所示，直至完成复位，柱塞2后移的过程中带动摆动杆7摆动，摆动杆7作用于第一杆91与第二杆92并带动冲头93沿竖直方向上移复位。
在本实施例中，压缩弹簧5采用非线性的蝶形弹簧，该蝶形弹簧在上述环形空间内套设在杆体41上并位于挡盖22与大直径端头42之间。由于蝶形弹簧的力学特性是非线性的，选用蝶形弹簧时可根据实际应用的工况来选取合理的力学特性区间，这样可以使得弹簧的复位力变化范围大幅度缩小，可有效地提高该柱塞缸的机械效率，有利于节能。而传统的拉伸螺旋弹簧由于其力学特征是线性的，其刚度与其变形量成正比，导致变形量较大时，其复位力显著变大，而这一复位力需要消耗额外提供给柱塞作用力来克服，势必将在系统压力一定的条件下，造成缸径扩大，本发明则很好地解决了这一问题，缸体的直径相比现有技术进一步减小。此外，蝶形弹簧可采用叠片的形式来提高刚度，这使得本发明的柱塞缸的输出力具有更大的调节范围，使其具有更好的通用性。
实施例2
参见图6、图7所示，该实施例与实施例1的区别仅在于柱塞2的设置，柱塞2的后端开设有可供杆体41穿入而大直径端头42不能穿入的通孔23，内孔21中位于大直径端头42与柱塞2后端内侧壁之间便形成了用于设置压缩弹簧5的环形空间。这相比实施例1仅为柱塞缸的生产与安装方式存在略微的差异，柱塞缸的工作原理与实施例1相同。
综上，本发明的单作用铰接内杆式柱塞缸，相比与传统的柱塞缸，由于柱塞2上铰接有摆动杆7，解决了传统柱塞缸只能输出往复直线运动的缺陷，其能够输出往复摆动等非直线运动，摆动杆7输出摆动力的过程中，柱塞2上受力均衡，力学特性良好。
由于将压缩弹簧设于柱塞2的内孔中，这相比在缸体外设置复位弹簧的柱塞缸，显著地减小了柱塞缸的整体结构尺寸。此外，该柱塞缸中由于采用压缩弹簧，其力学特性为非线性的，因此其复位力的变化范围幅度小，相应地提高了该柱塞缸的机械效率，使得该柱塞缸的力传递效率得到提高，有利于节能。本发明的柱塞缸部件较少，且制造和装配工艺性好，生产成本低。
实施例3
参见图8至图10所示的双作用缸，可为液压缸或气缸，其包括缸体1、固设于缸体1后端的后端盖3、固设于缸体1前端的前端盖301，以及设于缸体1中的活塞杆201，活塞杆201将缸体1的内腔分隔形成相隔绝的左压力腔和右压力腔。后端盖3上设有与左压力腔连通的第一注油孔/进气孔31，前端盖301上设有与右压力腔连通的第二注油孔/进气孔3011，通过电磁阀8控制向左压力腔或右压力腔中供油或供气，可驱动活塞杆201相对缸体1前后移动。
活塞杆201上开设有内孔21，该内孔中固定地设有铰支座6，在这里内孔21设为沿前后方向贯穿活塞杆201的通孔，铰支座6与内孔21的周向侧壁密封连接设置，在安装时可通过过盈配合的方式将铰支座6设于内孔21中。
铰支座6的前端铰接有摆动杆7，摆动杆7的后端可通过销轴铰接在铰支座6上，也可以按照球头铰接的方式铰接在铰支座6上。内孔21的前端呈圆锥状设置，该圆锥状为由后向前孔径逐渐增大的设置，以对摆动杆7的摆动进行让位。摆动杆7的前端位于内孔21的外侧，摆动杆7的前端则连接用于动力输出的输出杆组9。
在本实施例中，该输出杆组9包括第一杆91、第二杆92、冲头93。第一杆91的一端铰接在机架上，其另一端铰接在摆动杆7的前端，第二杆92的一端铰接在摆动杆7的前端，其另一端铰接在冲头93上，冲头93可沿竖直方向升降地设于机架上。
在初始状态时，如图8所示，活塞杆201位于缸体1的后部。当需要活塞杆201前移时，如图9所示，电磁阀8换向，左压力腔注入液压油或充入压缩气体，右压力腔中的液压油逐渐回流至油箱或压缩气体通入空气，活塞杆201向前移动，活塞杆201前移时作用于摆动杆7，而摆动杆7则在内孔21中摆动并作用于第一杆91、第二杆92，带动第一杆91和第二杆92摆动并驱动冲头93向下移动实现冲击，如图10所示。
当活塞杆201向前运动结束后，电磁阀8换向，再向右压力腔中注入液压油或充入压缩气体，活塞杆201逐渐向后移动，直至完成复位，活塞杆201后移的过程中带动摆动杆7摆动，摆动杆7作用于第一杆91与第二杆92并带动冲头93沿竖直方向上移复位。
当然，当输出杆组9为其他机构时，摆动杆7可根据其连接的机构的需要输出往复摆动或其他非直线运动。
综上，根据本发明的铰接内杆式液压缸或气缸，相比传统的液压缸与气缸，由于活塞杆开设内孔，并将摆动杆铰接在内孔中的铰支座上，解决了传统的液压缸与气缸仅能输出往复直线运动的缺陷，该铰接内杆式缸能够输出往复摆动等非直线运动。这相比传统的固定式液压缸与气缸的活塞杆的前端铰接连杆的方式，极大地缩小了轴向尺寸；而相比后端铰接式的液压缸或气缸，摆动部分质量大幅降低，从而大幅度地降低冲击所带来的负面影响。
上述实施例只为说明本发明的技术构思及特点，其目的在于让熟悉此项技术的人士能够了解本发明的内容并据以实施，并不能以此限制本发明的保护范围。凡根据本发明精神实质所作的等效变化或修饰，都应涵盖在本发明的保护范围之内。

Claims (14)

1. 一种单作用铰接内杆式柱塞缸，包括缸体、后端盖和柱塞，其特征在于：所述柱塞中开设有内孔，所述内孔中穿设有导杆组件，所述导杆组件包括杆体和固定地设于所述杆体前端的大直径端头，所述杆体的后端固定地连接在所述后端盖上，所述大直径端头可相对所述柱塞移动地设于所述内孔中，所述柱塞的后端与所述大直径端头之间形成环形空间，所述环形空间内设有压缩弹簧，所述内孔中固定地设有铰支座，所述铰支座在所述内孔中位于所述大直径端头的前方，所述铰支座的前端铰接有摆动杆。
2. 根据权利要求1所述的单作用铰接内杆式柱塞缸，其特征在于：所述内孔的前端呈圆锥状。
3. 根据权利要求1所述的单作用铰接内杆式柱塞缸，其特征在于：所述压缩弹簧为非线性蝶形弹簧。
4. 根据权利要求1所述的单作用铰接内杆式柱塞缸，其特征在于：所述铰支座在所述内孔中与所述内孔的周向侧壁密封接触。
5. 根据权利要求1所述的单作用铰接内杆式柱塞缸，其特征在于：所述摆动杆的后端通过销轴铰接在所述铰支座上。
6. 根据权利要求1所述的单作用铰接内杆式柱塞缸，其特征在于：所述柱塞的后端开设有可供所述杆体穿过的通孔，所述柱塞的后端内侧壁与所述大直径端头之间形成所述环形空间。
7. 根据权利要求1所述的单作用铰接内杆式柱塞缸，其特征在于：所述柱塞上所述内孔沿前后方向贯穿所述柱塞，所述内孔的后端固定地设有挡盖，所述挡盖与所述大直径端头之间形成所述环形空间。
8. 根据权利要求1所述的单作用铰接内杆式柱塞缸，其特征在于：所述大直径端头与所述杆体一体设置，或者所述大直径端头与所述杆体固定连接设置。
9. 一种铰接内杆式双作用缸，包括缸体、后端盖、前端盖、活塞杆，其特征在于：所述活塞杆上开设有内孔，所述内孔中固定地设有铰支座，所述铰支座的前端铰接有摆动杆。
10. 根据权利要求9所述的铰接内杆式双作用缸，其特征在于：所述活塞杆上所述内孔的前端呈圆锥状。
11. 根据权利要求9所述的铰接内杆式双作用缸，其特征在于：所述内孔为通孔，所述铰支座与所述内孔的周向侧壁密封连接设置。
12. 根据权利要求9所述的铰接内杆式双作用缸，其特征在于：所述摆动杆的前端穿出所述内孔外侧。
13. 根据权利要求1所述的铰接内杆式双作用缸，其特征在于：所述摆动杆的后端销铰在所述铰支座上。
14. 根据权利要求1所述的铰接内杆式双作用缸，其特征在于：所述摆动杆的后端球铰在所述铰支座上。
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