EP3835600B1 - Hydraulic cylinder - Google Patents
Hydraulic cylinder Download PDFInfo
- Publication number
- EP3835600B1 EP3835600B1 EP19859799.9A EP19859799A EP3835600B1 EP 3835600 B1 EP3835600 B1 EP 3835600B1 EP 19859799 A EP19859799 A EP 19859799A EP 3835600 B1 EP3835600 B1 EP 3835600B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- pressure
- pressure chamber
- fluid
- chamber
- cylinder
- 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.)
- Active
Links
- 239000012530 fluid Substances 0.000 claims description 127
- 238000004891 communication Methods 0.000 claims description 93
- 238000005192 partition Methods 0.000 claims description 29
- 238000001514 detection method Methods 0.000 claims description 26
- 230000007246 mechanism Effects 0.000 claims description 17
- 230000000149 penetrating effect Effects 0.000 claims description 6
- 238000000638 solvent extraction Methods 0.000 claims 4
- 238000000034 method Methods 0.000 description 46
- 238000012856 packing Methods 0.000 description 41
- 238000003780 insertion Methods 0.000 description 11
- 230000037431 insertion Effects 0.000 description 11
- 230000000903 blocking effect Effects 0.000 description 4
- 238000010586 diagram Methods 0.000 description 4
- 230000000694 effects Effects 0.000 description 4
- 239000013013 elastic material Substances 0.000 description 2
- 229910000838 Al alloy Inorganic materials 0.000 description 1
- 230000001419 dependent effect Effects 0.000 description 1
- 238000005265 energy consumption Methods 0.000 description 1
- 239000007788 liquid Substances 0.000 description 1
- 238000012423 maintenance Methods 0.000 description 1
- 230000007257 malfunction Effects 0.000 description 1
- 239000007769 metal material Substances 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 230000001105 regulatory effect Effects 0.000 description 1
- 238000007789 sealing Methods 0.000 description 1
- 239000013589 supplement Substances 0.000 description 1
- 238000011144 upstream manufacturing Methods 0.000 description 1
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 1
Images
Classifications
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- 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
- F15B15/20—Other details, e.g. assembly with regulating devices
- F15B15/204—Control means for piston speed or actuating force without external control, e.g. control valve inside the piston
-
- 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
- F15B15/1428—Cylinders
-
- 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
- F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
- F15B11/02—Systems essentially incorporating special features for controlling the speed or actuating force of an output member
- F15B11/028—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the actuating force
- F15B11/036—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the actuating force by means of servomotors having a plurality of working chambers
- F15B11/0365—Tandem constructions
-
- 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
- F15B13/00—Details of servomotor systems ; Valves for servomotor systems
- F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
- F15B13/027—Check valves
-
- 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
-
- 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
- F15B15/00—Fluid-actuated devices for displacing a member from one position to another; Gearing associated therewith
- F15B15/20—Other details, e.g. assembly with regulating devices
-
- 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
- F15B2211/30—Directional control
- F15B2211/305—Directional control characterised by the type of valves
- F15B2211/30505—Non-return valves, i.e. check valves
-
- 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
- F15B2211/30—Directional control
- F15B2211/305—Directional control characterised by the type of valves
- F15B2211/3056—Assemblies of multiple valves
- F15B2211/30565—Assemblies of multiple valves having multiple valves for a single output member, e.g. for creating higher valve function by use of multiple valves like two 2/2-valves replacing a 5/3-valve
- F15B2211/3058—Assemblies of multiple valves having multiple valves for a single output member, e.g. for creating higher valve function by use of multiple valves like two 2/2-valves replacing a 5/3-valve having additional valves for interconnecting the fluid chambers of a double-acting actuator, e.g. for regeneration mode or for floating mode
-
- 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
- F15B2211/40—Flow control
- F15B2211/405—Flow control characterised by the type of flow control means or valve
- F15B2211/40515—Flow control characterised by the type of flow control means or valve with variable throttles or orifices
-
- 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
- F15B2211/40—Flow control
- F15B2211/415—Flow control characterised by the connections of the flow control means in the circuit
- F15B2211/41554—Flow control characterised by the connections of the flow control means in the circuit being connected to a return line and a directional control valve
-
- 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
- F15B2211/7055—Linear output members having more than two chambers
- F15B2211/7056—Tandem cylinders
-
- 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
- F15B2211/775—Combined control, e.g. control of speed and force for providing a high speed approach stroke with low force followed by a low speed working stroke with high force, e.g. for a hydraulic press
-
- 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
- F15B2211/80—Other types of control related to particular problems or conditions
- F15B2211/885—Control specific to the type of fluid, e.g. specific to magnetorheological fluid
- F15B2211/8855—Compressible fluids, e.g. specific to pneumatics
Definitions
- the present invention relates to a fluid pressure cylinder (hydraulic cylinder).
- a fluid pressure cylinder described in Japanese Laid-Open Patent Publication No. 2018-017269 includes a booster piston serving as a booster mechanism, and the booster piston is locked onto a piston rod in the middle of a stroke to thereby increase thrust force.
- An actuator assembly known from EP 2 314 884 A2 comprises a first cylinder housing a first piston and a second cylinder housing a second piston.
- the first and second pistons are coupled together, and the first cylinder is provided with a selectively closable conduit enabling fluid to flow from one side of the first piston to the other and a flow restrictor enabling the rate of fluid flow through the conduit to be selectively controlled.
- the flow restrictor may serve to selectively close the conduit.
- the second conduit may have a larger flow capacity than the first conduit.
- the actuator may be operated by compressed air or gas, or another suitable fluid, for example a liquid such as oil or water.
- the actuator assembly may be provided with a control means to automatically control its operation.
- Document US 2017/0108014 A1 discloses a hydraulic drive comprising a working cylinder and a travel cylinder which is mechanically connected to the working cylinder.
- the working cylinder and the travel cylinder each comprise an upper and a lower cylinder chamber, and all four cylinder chambers of the working and travel cylinder are connected to one another in a suitable manner in a closed pressure circuit which is filled and prestressed with a hydraulic fluid.
- a rotational speed-variable hydraulic machine with a first and second pressure connection is arranged in the pressure circuit in order to conduct the hydraulic fluid between the individual cylinder chambers of the working and travel cylinder during the operation of the hydraulic drive.
- At least one first and second distributing valve are arranged in the pressure circuit such that the respective valve switch positions which are suitable for the different operating phases of the hydraulic drive together with the suitably driven hydraulic machine allow a common movement of the work and travel cylinder in one or the other piston movement direction.
- the first and the second distributing valve are arranged in the pressure circuit.
- the present invention has been devised taking into consideration the aforementioned problem, and has the object of providing a fluid pressure cylinder with a booster function, which is capable of reducing the consumption of working fluid without complicated structures.
- a fluid pressure cylinder comprising the features of claim 1 or 3.
- a fluid pressure cylinder 10 includes a cylinder body 12 and a drive device 120.
- the fluid pressure cylinder 10 includes the cylinder body 12 extending in the axial direction.
- the cylinder body 12 may have a rectangular shape as illustrated in FIG. 2 and is composed of, for example, a metal material such as aluminum alloy.
- the cylinder body 12 contains, formed therein, a circular slide hole 12a (cylinder chamber) extending in the axial direction.
- the cylinder body 12 includes a head-side body portion 14 disposed on the head side, an end-side body portion 16 disposed on the end side, and a partition wall 26 disposed between the head-side body portion 14 and the end-side body portion 16.
- the head-side body portion 14, the partition wall 26, and the end-side body portion 16 are fastened together in the axial direction by connecting rods or bolts 16b.
- the head-side body portion 14 contains, formed therein, a circular working cylinder chamber 14a
- the end-side body portion 16 contains, formed therein, a circular booster cylinder chamber 16a.
- the working cylinder chamber 14a and the booster cylinder chamber 16a have an identical inner diameter and constitute the slide hole 12a of the cylinder body 12.
- the working cylinder chamber 14a and the booster cylinder chamber 16a are separated by the partition wall 26.
- a working piston 20 is disposed in the working cylinder chamber 14a, and a booster piston 22 is disposed in the booster cylinder chamber 16a.
- the working piston 20 and the booster piston 22 are connected to a piston rod 18 extending toward the end side and penetrating through the partition wall 26 and the cylinder body 12.
- the head-side body portion 14 is provided with a head-side port 28, a head cover 46, and the working piston 20.
- the head cover 46 is attached to the head-side end of the working cylinder chamber 14a, and seals the head side of the working cylinder chamber 14a.
- the head-side port 28 is provided adjacent to the head cover 46.
- the head-side port 28 penetrates through the head-side body portion 14.
- the head-side port 28 communicates with the working cylinder chamber 14a (first pressure chamber 38) via an opening 28a provided adjacent to the head-side end of the working cylinder chamber 14a.
- the working piston 20 is accommodated inside the working cylinder chamber 14a so as to be slidable in the axial direction.
- An annular packing receiving groove 21a is formed in the outer circumferential surface of the working piston 20, and a packing 21 is disposed into the packing receiving groove 21a.
- the packing 21 comes into close contact with the inner circumferential surface of the working cylinder chamber 14a while elastically deforming, and thereby airtightly partitions the working cylinder chamber 14a into the first pressure chamber 38 and a second pressure chamber 40.
- the first pressure chamber 38 is an empty chamber formed between the working piston 20 and the head cover 46 and is located on the head side of the working piston 20.
- the second pressure chamber 40 is an empty chamber formed between the working piston 20 and the partition wall 26 and is located on the end side of the working piston 20.
- the first pressure chamber 38 communicates with the head-side port 28 via the opening 28a.
- the working piston 20 is connected to the piston rod 18 at a head-side connection portion 18a of the piston rod 18 and displaceable integrally with the piston rod 18.
- the end-side body portion 16 is provided with the booster piston 22, a rod cover 48, an end-side port 30, and an auxiliary path 76.
- the booster piston 22 is disposed inside the booster cylinder chamber 16a in the end-side body portion 16 so as to be slidable in the axial direction.
- An annular packing receiving groove 23a and an annular magnet receiving groove 24a are formed in the outer circumferential surface of the booster piston 22.
- An annular packing 23 composed of an elastic material such as rubber is mounted into the packing receiving groove 23a.
- a circular ring-shaped magnet 24 is mounted into the magnet receiving groove 24a.
- a wear ring (not illustrated) is attached to an outer circumferential portion of the magnet 24.
- the booster piston 22 airtightly partitions the booster cylinder chamber 16a into a third pressure chamber 42 and a fourth pressure chamber 44 via the packing 23.
- the third pressure chamber 42 is an empty chamber formed between the booster piston 22 and the partition wall 26 and is located on the head side of the booster piston 22.
- the fourth pressure chamber 44 is an empty chamber formed between the booster piston 22 and the rod cover 48 and is located on the end side of the booster piston 22.
- the fourth pressure chamber 44 communicates with the end-side port 30.
- An annular damper receiving groove 25a is formed in the head-side end face of the booster piston 22, and a damper 25 is mounted into the damper receiving groove 25a.
- the damper 25 is composed of an elastic material such as rubber and is configured to prevent collision of the booster piston 22 with the partition wall 26.
- the booster piston 22 is connected to a piston attachment portion 18b located in the midsection of the piston rod 18 and is displaceable in the axial direction integrally with the piston rod 18.
- the rod cover 48 is attached to an end-side part of the booster cylinder chamber 16a.
- the rod cover 48 has a disk shape and includes an annular packing receiving groove 48d formed in an outer circumferential part thereof.
- a circular ring-shaped packing 48c is mounted into the packing receiving groove 48d.
- the packing 48c airtightly seals the packing receiving groove 48d.
- the rod cover 48 has an insertion hole 48a in the vicinity of the radial center.
- the insertion hole 48a extends in the axial direction, and the piston rod 18 passes therethrough.
- a rod packing 48b is disposed in the insertion hole 48a to prevent leakage of air along the piston rod 18.
- An annular damper receiving groove 47a is formed in the head-side end face of the rod cover 48, and a damper 47 is mounted into the damper receiving groove 47a.
- the damper 47 is composed of an elastic member having a circular ring shape. The damper 47 protrudes toward the interior of the booster cylinder chamber 16a to prevent collision of the rod cover 48 with the booster piston 22.
- a retaining clip 49 is attached to an end-side part of the rod cover 48 to secure the rod cover 48.
- the retaining clip 49 is a plate member engaged into an engaging groove 49a formed in the end-side body portion 16 along the inner circumferential surface of the end-side body portion 16.
- the retaining clip 49 is an annular plate member having a gap at a circumferential position. The retaining clip is engaged into the engaging groove 49a by the elastic restoring force and is in contact with the end-side end face of the rod cover 48, thereby preventing the rod cover 48 from coming off.
- the end-side port 30 is formed in the end-side body portion 16 adjacent to the end-side end.
- the end-side port 30 penetrates through the end-side body portion 16 from the outer circumference to the booster cylinder chamber 16a and communicates with the fourth pressure chamber 44 at an end-side end part of the booster cylinder chamber 16a.
- the auxiliary path 76 is a flow path formed inside the end-side body portion 16 and extends in the axial direction. A first end of the auxiliary path 76 communicates with the end-side port 30, and a second end thereof communicates with an adjustment port 32 (described below) in the partition wall 26.
- a third check valve 56 is disposed at a position on the auxiliary path 76.
- the third check valve 56 includes a hollow portion 56a having a larger diameter than the auxiliary path 76 and a valve element 56b inserted into the hollow portion 56a.
- the valve element 56b is a cup-shaped member having a cylindrical shape with a bottom, and the bottom 56c is disposed downstream in an airflow that is to be blocked.
- the bottom 56c of the valve element 56b includes an annular protrusion 56d which is brought into contact with an end face of the hollow portion 56a to thereby block the auxiliary path 76 communicating with the hollow portion 56a.
- a cutout portion 56e is formed in a side part of the valve element 56b to allow air to pass.
- the annular protrusion 56d of the valve element 56b is configured to be separated from the end face of the hollow portion 56a to thereby pass the air via the cutout portion 56e.
- the bottom 56c of the valve element 56b is configured to receive the pressure of the air to thereby bring the annular protrusion 56d into contact with the end face of the hollow portion 56a and block the auxiliary path 76, so that the airflow is stopped.
- a biasing member 56f such as a spring may be disposed inside the hollow portion 56a to bias the annular protrusion 56d of the valve element 56b toward the end face of the hollow portion 56a.
- a first check valve 52 and a second check valve 54 described below have structures similar to that of the third check valve 56.
- the partition wall 26 includes a plate-shaped body 60.
- the body 60 includes a first connection part 63 protruding toward the head side so as to be inserted into the working cylinder chamber 14a and a second connection part 64 protruding toward the end side so as to be inserted into the booster cylinder chamber 16a.
- the first connection part 63 has a circular cylindrical shape having an outer diameter substantially equal to the inner diameter of the working cylinder chamber 14a.
- a packing 63a is attached to an outer circumferential part of the first connection part 63.
- the second connection part 64 has a circular cylindrical shape having an outer diameter substantially equal to the inner diameter of the booster cylinder chamber 16a.
- a packing 64a is attached to an outer circumferential part of the second connection part 64.
- the packing 63a seals the gap between the working cylinder chamber 14a and the first connection part 63.
- the packing 64a seals the gap between the booster cylinder chamber 16a and the second connection part 64.
- the partition wall 26 includes a through-hole part 61 in the vicinity of the radial center.
- the through-hole part 61 extends in the axial direction, and the piston rod 18 passes therethrough.
- a packing 62 is disposed in the through-hole part 61 to prevent leakage of air along the piston rod 18.
- the partition wall 26 further includes a communication path 34, a communication switching valve 35 disposed in the communication path 34, an exhaust path 36, and an exhaust switching valve 37 disposed in the exhaust path 36, which form a boost switching mechanism 33.
- the communication path 34 is a flow path that allows air to flow between the second pressure chamber 40 and the third pressure chamber 42.
- the communication path 34 includes a through-hole 65 penetrating through the partition wall 26 in the axial direction, an inner channel 35e of a communication switching pin 35a inserted into the through-hole 65, and a hole 66b of a stopper 66.
- the through-hole 65 penetrates through the partition wall 26 in the axial direction and includes a large-diameter part 65a disposed on the head side, a small-diameter part 65b disposed in the middle in the axial direction, and a stopper insertion hole 65c disposed on the end side.
- the large-diameter part 65a and the stopper insertion hole 65c have larger inner diameters than the small-diameter part 65b.
- the communication switching pin 35a is disposed inside the large-diameter part 65a and the small-diameter part 65b.
- the stopper 66 is inserted into the stopper insertion hole 65c.
- the stopper 66 is connected to an end-side part of the communication switching pin 35a of the communication switching valve 35 and is displaced integrally with the communication switching pin 35a. Movement of the communication switching pin 35a toward the head side is restricted when the stopper 66 stops inside the stopper insertion hole 65c.
- the communication switching valve 35 includes the communication switching pin 35a.
- the communication switching pin 35a includes a closing part 35c disposed on the head side and a rod part 35d extending in the axial direction toward the end side.
- the rod part 35d has a diameter substantially equal to the inner diameter of the small-diameter part 65b of the through-hole 65, and the rod part is inserted into the small-diameter part 65b so as to be slidable in the axial direction.
- the closing part 35c has a diameter substantially equal to the inner diameter of the large-diameter part 65a of the through-hole 65 so as to be insertable into the large-diameter part 65a.
- a ring-shaped packing 35b is attached to an outer circumferential part of the closing part 35c. When the closing part 35c is pushed into the large-diameter part 65a, the packing 35b comes into close contact with the large-diameter part 65a and thereby seals the communication path 34.
- a biasing member 35f is attached to the end side of the closing part 35c of the communication switching pin 35a.
- the biasing member 35f is formed by, for example, a spring, and disposed in the gap between the large-diameter part 65a and the communication switching pin 35a.
- the biasing member 35f biases the communication switching pin 35a toward the head side such that the closing part 35c is separated from the through-hole 65 and protrudes into the second pressure chamber 40. That is, the communication switching valve 35 does not block the communication path 34 in a state that the communication switching pin 35a is not pushed, by the working piston 20, toward the end side.
- the exhaust path 36 has an opening on an end face of the partition wall 26 on the first connection part 63 side.
- the exhaust path 36 includes a detection-pin accommodating hole 67 extending in the axial direction and a connecting channel 71 communicating with both the detection-pin accommodating hole 67 and the adjustment port 32.
- the detection-pin accommodating hole 67 includes a large-diameter part 67a disposed on the head side, a small-diameter part 67b disposed on the end side of the large-diameter part 67a, and a stopper insertion hole 67c.
- a stopper 68 is inserted into the stopper insertion hole 67c.
- the stopper 68 is connected to a detection pin 37a and is displaced integrally with the detection pin 37a. The moving range of the detection pin 37a toward the head side is limited when the stopper 68 stops at the end-side end of the small-diameter part 67b.
- the connecting channel 71 communicates with the detection-pin accommodating hole 67 at an opening part 71a formed in a side part of the small-diameter part 67b.
- the diameter of the small-diameter part 67b is increased in a predetermined region around the opening part 71a, so that a gap is left between the small-diameter part 67b and the exhaust switching valve 37.
- the first check valve 52 which allows air to flow only in a direction from the opening part 71a toward the adjustment port 32, is disposed in the connecting channel 71.
- the first check valve 52 is disposed in a direction so as to allow air from the second pressure chamber 40 to be discharged.
- the exhaust switching valve 37 includes the detection pin 37a.
- the detection pin 37a includes a pin body part 37b having a circular cylindrical shape extending in the axial direction and a flange part 37c extending radially outward from the head-side end of the pin body part 37b.
- the flange part 37c has a diameter slightly smaller than the inner diameter of the large-diameter part 67a and is formed so as to be insertable into the large-diameter part 67a.
- a biasing member 37f formed by, for example, a spring is disposed in the large-diameter part 67a. The biasing member 37f is in contact with the flange part 37c and biases the detection pin 37a toward the head side, so that the flange part 37c protrudes into the second pressure chamber 40.
- the pin body part 37b has a diameter slightly smaller than the inner diameter of the small-diameter part 67b and is configured to be slidable in the axial direction along the small-diameter part 67b.
- a packing 37d and a packing 37e are disposed on an outer circumferential part of the pin body part 37b at a distance from each other in the axial direction.
- the packing 37d and the packing 37e are placed at positions where the packings are in close contact with the small-diameter part 67b to thereby block the communication between the detection-pin accommodating hole 67 and the connecting channel 71. That is, the exhaust switching valve 37 blocks the exhaust path 36 in the state that the exhaust switching valve 37 is not pushed by the working piston 20.
- a supplementary channel 78 and the second check valve 54 are provided in the head-side body portion 14 adjacent to the adjustment port 32.
- the supplementary channel 78 communicates with the adjustment port 32 and the second pressure chamber 40.
- the second check valve 54 is disposed in the supplementary channel 78.
- a first end of the second check valve 54 communicates with the adjustment port 32 via the supplementary channel 78.
- a second end of the second check valve 54 communicates with the second pressure chamber 40 via the supplementary channel 78.
- the second check valve 54 allows air to flow only in a direction from the adjustment port 32 toward the second pressure chamber 40 and blocks flow of air in the opposite direction. That is, the second check valve 54 allows air for supplement to the second pressure chamber 40 to flow and blocks air flowing in the opposite direction.
- the fluid pressure cylinder 10 of this embodiment is configured as above and operated by the drive device 120 as illustrated in FIG. 4A .
- the drive device 120 includes a fourth check valve 86, a throttle valve 88, a switching valve 102, a high-pressure-air supply source (high-pressure-fluid supply source) 104, and an exhaust port 106.
- the drive device 120 is configured to supply high-pressure air to the first pressure chamber 38 in the working cylinder chamber 14a during the working process.
- the drive device 120 is configured to supply high-pressure air to the second pressure chamber 40 while supplying part of air accumulated in the first pressure chamber 38 to the fourth pressure chamber 44 during the return process.
- the switching valve 102 is, for example, a 5-port, 2-position valve including a first port 102a to a fifth port 102e and is switchable between a first position (see FIG. 4A ) and a second position (see FIG. 4B ).
- the first port 102a is connected to the head-side port 28 by pipes.
- the second port 102b is connected to the adjustment port 32 by pipes.
- the third port 102c is connected to the exhaust port 106 by pipes.
- the fourth port 102d is connected to the high-pressure-air supply source 104 by pipes.
- the fifth port 102e is connected to the exhaust port 106 via the throttle valve 88 and to the end-side port 30 via the fourth check valve 86 by pipes.
- the switching valve 102 when the switching valve 102 is in the first position, the first port 102a is connected to the fourth port 102d, and the second port 102b is connected to the third port 102c.
- the switching valve 102 when the switching valve 102 is in the second position, the first port 102a is connected to the fifth port 102e, and the second port 102b is connected to the fourth port 102d.
- the switching valve 102 is switched between the first position and the second position by pilot pressure from the high-pressure-air supply source 104 or by a solenoid valve.
- the fourth check valve 86 allows air to flow from the head-side port 28 to the end-side port 30 and blocks air flowing from the end-side port 30 toward the head-side port 28.
- the throttle valve 88 which is an adjustable throttle valve of which path area can be changed to adjust the exhaust flow rate, limits the amount of air discharged from the first pressure chamber 38 through the exhaust port 106.
- An air tank may be disposed at a position along a pipe connecting the fourth check valve 86 and the fourth pressure chamber 44 to thereby accumulate air supplied from the head-side port 28 to the end-side port 30 during the return process.
- the air tank can accumulate air sufficient to fill the fourth pressure chamber 44 during the return operation, resulting in a stable return operation.
- the volume of the air tank may be set to, for example, about half the maximum volume of the first pressure chamber 38. The air tank is unnecessary in a case where the pipes have sufficient volume.
- the fluid pressure cylinder 10 and the drive device 120 are configured as above. Next, the effects and operations thereof will be described.
- the second pressure chamber 40 and the third pressure chamber 42 are filled with high-pressure air.
- the high-pressure air refers to air at a pressure higher than atmospheric pressure.
- the fluid pressure cylinder 10 is set in the start-of-stroke position as illustrated in FIG. 1 .
- the switching valve 102 of the drive device 120 is in the second position (see FIG. 4B ).
- the high-pressure-air supply source 104 is thus connected to the adjustment port 32.
- high-pressure air is introduced from the high-pressure-air supply source 104 into the second pressure chamber 40 via the second check valve 54.
- the high-pressure air introduced into the second pressure chamber 40 is also introduced into the third pressure chamber 42 via the communication path 34.
- the second pressure chamber 40 and the third pressure chamber 42 are filled with high-pressure air.
- the startup process may be performed only once before the first stroke of the fluid pressure cylinder 10.
- the switching valve 102 of the drive device 120 is set in the first position as illustrated in FIG. 4A .
- High-pressure air is supplied from the high-pressure-air supply source 104 to the head-side port 28 via the first port 102a of the switching valve 102.
- High-pressure air does not flow toward the fourth check valve 86 since the fourth check valve 86 is connected to the fifth port 102e.
- the fourth pressure chamber 44 is connected to the exhaust port 106 via the third check valve 56, the adjustment port 32, and the second port 102b.
- high-pressure air from the high-pressure-air supply source 104 flows into the first pressure chamber 38 as indicated by an arrow B.
- Force exerted on the working piston by the high-pressure air in the second pressure chamber 40 and force exerted on the booster piston 22 by the high-pressure air that fills the third pressure chamber 42 are equal in magnitude and balanced in the opposite direction.
- the forces do not contribute to thrust force.
- thrust force corresponding to a difference between the pressure in the first pressure chamber 38 adjoining the working piston 20 and the pressure in the fourth pressure chamber 44 adjoining the booster piston 22 acts on the piston rod 18, and the piston rod 18 moves toward the end side.
- high-pressure air of an amount equal to the volume of the first pressure chamber 38 is supplied from the high-pressure-air supply source 104 (see FIG. 4A ) to the fluid pressure cylinder 10.
- the high-pressure air inside the second pressure chamber 40 moves to the third pressure chamber 42 via the communication path 34.
- the pressure of the high-pressure air stored in the second pressure chamber 40 and the pressure of the high-pressure air stored in the third pressure chamber 42 are kept constant.
- air in the fourth pressure chamber 44 is discharged from the fourth pressure chamber 44 as the booster piston 22 moves.
- the air in the fourth pressure chamber 44 passes through the adjustment port 32 via the third check valve 56 and the auxiliary path 76, and is discharged from the exhaust port 106 through the second port 102b of the switching valve 102 as illustrated in FIG. 4A .
- the closing part 35c of the communication switching pin 35a is inserted into the large-diameter part 65a of the through-hole 65.
- the packing 35b on the closing part 35c seals the gap between the large-diameter part 65a and the closing part 35c, thereby blocking the communication path 34. That is, the communication switching valve 35 blocks the communication of air between the second pressure chamber 40 and the third pressure chamber 42 via the communication path 34.
- the packing 37d that has sealed the gap between the detection pin 37a and the detection-pin accommodating hole 67 moves to the recessed opening part 71a.
- This movement opens the exhaust path 36, and the adjustment port 32 and the second pressure chamber 40 communicate with each other via the exhaust path 36.
- the high-pressure air stored in the second pressure chamber 40 is discharged from the exhaust port 106 via the first check valve 52 and the adjustment port 32.
- the internal pressure in the second pressure chamber 40 drops, and thrust force corresponding to a difference between the internal pressure in the second pressure chamber 40 and the internal pressure in the first pressure chamber 38 acts on the working piston 20.
- thrust force corresponding to a difference between the pressure of the high-pressure air stored in the third pressure chamber 42 and the pressure in the fourth pressure chamber 44 acts on the booster piston 22.
- the fluid pressure cylinder 10 can increase the thrust force near the stroke end.
- the thrust force is increased by the discharge of the high-pressure air in the second pressure chamber 40 while the communication switching valve 35 and the exhaust switching valve 37 are being actuated.
- the switching valve 102 of the drive device 120 is set in the second position as illustrated in FIG. 4B .
- High-pressure air is supplied from the high-pressure-air supply source 104 to the adjustment port 32 via the second port 102b of the switching valve 102.
- the first port 102a of the switching valve 102 is connected to the fifth port 102e, and thereby the head-side port 28 is connected to the end-side port 30 via the fourth check valve 86.
- the head-side port 28 is also connected to the exhaust port 106 via the throttle valve 88.
- part of the air stored in the first pressure chamber 38 is supplied to the fourth pressure chamber 44 via the route with the fourth check valve 86.
- the remaining part of the air stored in the first pressure chamber 38 is discharged from the exhaust port 106.
- high-pressure air from the high-pressure-air supply source 104 is supplied to the adjustment port 32 of the fluid pressure cylinder 10 as indicated by an arrow B.
- the high-pressure air supplied to the adjustment port 32 flows into the second pressure chamber 40 through the supplementary channel 78 and the second check valve 54.
- the volume of the high-pressure air supplied to the second pressure chamber 40 is equal to the volume of the high-pressure air discharged from the second pressure chamber 40 during the boosting process. That is, high-pressure air required for the boosting process is supplemented during the return process.
- the amount of high-pressure air supplied at this moment is small compared with the volume of the high-pressure air required for movement of the working piston 20, and thus only a small addition of high-pressure air is required.
- part of the high-pressure air discharged from the first pressure chamber 38 flows into the fourth pressure chamber 44 as indicated by an arrow A.
- the difference between the pressure in the fourth pressure chamber 44 and the pressure in the first pressure chamber 38 increases, and the working piston 20, the booster piston 22, and the piston rod 18 start moving toward the head side.
- the communication switching valve 35 returns to its original position, and the second pressure chamber 40 and the third pressure chamber 42 communicate with each other through the communication path 34.
- the exhaust switching valve 37 seals the exhaust path 36 and blocks the communication between the adjustment port 32 and the second pressure chamber 40.
- the fluid pressure cylinder 10 according to this embodiment produces the following advantageous effects.
- the fluid pressure cylinder 10 includes, as the boost switching mechanism 33, the communication path 34 communicating with the second pressure chamber 40 and the third pressure chamber 42, the exhaust path 36 communicating with the second pressure chamber 40, the communication switching valve 35 configured to open the communication path 34 when the working piston 20 is located on the head side of a predetermined position and configured to close the communication path 34 when the working piston 20 moves to the end side of the predetermined position, and the exhaust switching valve 37 configured to close the exhaust path 36 when the working piston 20 is located on the head side of the predetermined position and configured to open the exhaust path 36 to discharge high-pressure fluid in the second pressure chamber 40 when the working piston 20 moves to the end side of the predetermined position.
- the partition wall 26 may include the adjustment port 32, and the exhaust path 36 may be configured to discharge the high-pressure fluid in the second pressure chamber 40 via the adjustment port 32.
- the boost switching mechanism 33 may be configured such that the exhaust switching valve 37 opens the exhaust path 36 after the communication switching valve 35 closes the communication path 34. This prevents the outflow of high-pressure air from the third pressure chamber 42 via the second pressure chamber 40, thereby reducing the consumption of high-pressure air.
- the communication switching valve 35 may include the communication switching pin 35a including the first end that protrudes into the second pressure chamber 40 and the second end that is inserted into the communication path 34, and may be configured to block the communication path 34 when the communication switching pin 35a is pushed by the working piston 20 and displaced toward the end side. This enables the communication switching valve 35 to operate using the stroke movement of the working piston 20, thereby simplifying the device structure.
- the exhaust switching valve 37 may include the detection pin 37a including the first end that protrudes into the second pressure chamber 40 and sealing the exhaust path 36, and may be configured to unseal or open the exhaust path 36 when the detection pin 37a is pushed by the working piston 20 and displaced toward the end side. This enables the air in the second pressure chamber 40 to be discharged via the exhaust path 36 using the stroke movement of the working piston 20, thereby simplifying the device structure.
- the exhaust path 36 may be provided with the first check valve 52 allowing air to flow only in a direction from the second pressure chamber 40 toward the adjustment port 32 and blocking air flowing in the opposite direction. This prevents malfunctions of the exhaust switching valve 37 during the return process.
- the fluid pressure cylinder 10 may further includes the supplementary channel 78 communicating with the adjustment port 32 and the second pressure chamber 40.
- the supplementary channel 78 may be provided with the second check valve 54 allowing air to flow only in a direction from the adjustment port 32 toward the second pressure chamber 40 and blocking air flowing in the opposite direction. Provision of the second check valve 54 prevents excessive inflow of high-pressure air into the second pressure chamber 40 during the return process.
- the fluid pressure cylinder 10 may further include the auxiliary path 76 communicating with the fourth pressure chamber 44 and the adjustment port 32. This enables the air in the fourth pressure chamber 44 to be discharged through the adjustment port 32 during the working process and the boosting process.
- the auxiliary path 76 may be provided with the third check valve 56 allowing air to flow only in a direction from the fourth pressure chamber 44 toward the adjustment port 32 and blocking air flowing in the opposite direction. This prevents high-pressure air from flowing into the fourth pressure chamber 44 when high-pressure air is supplied to the adjustment port 32 during the return process, thereby reducing the consumption of high-pressure air.
- the fluid pressure cylinder 10 may further include the drive device 120 connected to the first pressure chamber 38, the second pressure chamber 40, and the fourth pressure chamber 44 of the fluid pressure cylinder 10.
- the drive device 120 may include the switching valve 102, the high-pressure-air supply source 104, the exhaust port 106, and the fourth check valve 86.
- the switching valve 102 When the switching valve 102 is in the first position, the first pressure chamber 38 may communicate with the high-pressure-air supply source 104, and the fourth pressure chamber 44 and the adjustment port 32 (boost switching mechanism 33) may communicate with the exhaust port 106.
- the first pressure chamber 38 may communicate with the fourth pressure chamber 44 via the fourth check valve 86 and with the exhaust port 106, and the second pressure chamber 40 may communicate with the high-pressure-air supply source 104 via the adjustment port 32. This enables the fourth pressure chamber 44 to be supplied with the air accumulated in the first pressure chamber 38 during the return process, thereby reducing the consumption of high-pressure air.
- the fluid pressure cylinder 10 may further include the throttle valve 88 disposed between the first pressure chamber 38 and the exhaust port 106. This allows the amount of air supplied to the fourth pressure chamber 44 to be appropriately adjusted.
- a fluid pressure cylinder 10A includes a head-side body portion 14A and an end-side body portion 16A.
- high-pressure fluid is enclosed in the end-side body portion 16A.
- the size (width and height) of the end-side body portion 16A is made larger than the size of the head-side body portion 14A.
- the head-side body portion 14A and the end-side body portion 16A have rectangular cross-sections.
- the head-side body portion 14A and the end-side body portion 16A are fastened together in the axial direction by connecting rods or bolts.
- a cylinder body 12A of the fluid pressure cylinder 10A includes the head-side body portion 14A and the end-side body portion 16A connected to each other in the axial direction via a partition wall 126.
- the head-side body portion 14A includes a head-side port 28A and an end-side port 30A.
- the end-side body portion 16A includes an adjustment port 32A adjacent to the end-side end.
- a stored-air exhaust port 162 is formed in a portion of the partition wall 126 adjacent to the outer circumference in order to discharge high-pressure air enclosed in a booster cylinder chamber 116a.
- the stored-air exhaust port 162 communicates with a third pressure chamber 42 via a regulating valve 160.
- the stored-air exhaust port 162 is used to discharge high-pressure air stored inside the booster cylinder chamber 116a during, for example, the maintenance of the fluid pressure cylinder 10A and to introduce high-pressure air into the booster cylinder chamber 116a at startup.
- An insertion hole 126c into which a piston rod 18A is slidably inserted is formed in a central part of the partition wall 126.
- a packing 118 is disposed in the insertion hole 126c to prevent leakage of fluid in the axial direction.
- the partition wall 126 includes a head-side connection part 126a protruding toward the head side and inserted into a working cylinder chamber 14a.
- the partition wall 126 further includes an end-side connection part 126b protruding toward the end side and inserted into the booster cylinder chamber 116a.
- An annular cushion member 124 is attached to the end-side connection part 126b to prevent the end-side connection part 126b from colliding with a booster piston 22A.
- the end-side body portion 16A includes a body part 116.
- the booster cylinder chamber 116a which is a circular cavity, is formed inside the body part 116.
- the booster cylinder chamber 116a extends in the axial direction.
- the booster piston 22A is disposed inside the booster cylinder chamber 116a so as to be slidable in the axial direction.
- the booster piston 22A is connected to the piston rod 18A.
- a magnet 24 and a packing 23 are attached to an outer circumferential part of the booster piston 22A.
- the booster piston 22A divides the booster cylinder chamber 116a into the third pressure chamber 42 on the head side and a fourth pressure chamber 44 on the end side.
- the booster piston 22A is provided with a communication switching valve 35A switching between communication and non-communication of high-pressure fluid between the third pressure chamber 42 and the fourth pressure chamber 44, which are adjacent to each other in the axial direction.
- the communication switching valve 35A includes a through-hole 122 penetrating through the booster piston 22A in the axial direction and a communication switching pin 35a inserted into the through-hole 122.
- the through-hole 122 includes an end-side large-diameter part 122a, a small-diameter part 122b, and a head-side large-diameter part 122c.
- the communication switching pin 35a of the communication switching valve 35A is similar to the communication switching pin 35a, which has been described with reference to FIG. 3A .
- a rod part 35d of the communication switching pin 35a is inserted into the small-diameter part 122b.
- a closing part 35c of the communication switching pin 35a is disposed on the end-side large-diameter part 122a side.
- the communication switching pin 35a protrudes toward the end side by biasing force of a biasing member 35f.
- High-pressure air can flow between the third pressure chamber 42 and the fourth pressure chamber 44 via the through-hole 122 and an inner channel 35e in the communication switching pin 35a. That is, in this embodiment, the through-hole 122 and the inner channel 35e constitute a communication path.
- the communication switching pin 35a is pushed against a rod cover 48A. This causes the closing part 35c and a packing 35b on an outer circumferential part of the closing part 35c to be inserted into the through-hole 122 to thereby close the through-hole 122. As a result, the communication between the third pressure chamber 42 and the fourth pressure chamber 44 is blocked.
- the rod cover 48A is disposed adjacent to the end-side end of the end-side body portion 16A and seals the end-side end of the booster cylinder chamber 116a.
- the rod cover 48A is provided with an exhaust switching valve 37A switching the discharge state of high-pressure air in the fourth pressure chamber 44.
- the exhaust switching valve 37A includes a through-hole 139 penetrating through the rod cover 48A in the axial direction and a detection pin 137 inserted into the through-hole 139.
- the end-side end of the through-hole 139 is sealed with a cover member 150, and the detection pin 137 is disposed on the head side of the cover member 150.
- the detection pin 137 is biased toward the head side by a biasing member 140 such as a spring disposed between the cover member 150 and the detection pin 137. This causes the distal end part of the detection pin 137 on the head side to protrude inside the fourth pressure chamber 44.
- Annular packings 141 and 142 are attached to an outer circumferential part of a basal end part 138 of the detection pin 137 at a distance from each other in the axial direction.
- the packings 141 and 142 seal the gap between the through-hole 139 and the detection pin 137.
- a channel 143 is disposed between the packings 141 and 142.
- the inner end of the channel 143 communicates with the through-hole 139, and the outer end thereof communicates with an air channel 144.
- the air channel 144 is an annular groove formed in an outer circumferential part of the rod cover 48A around the entire circumference and communicates with the adjustment port 32A.
- a packing 146 is disposed on the head side of the air channel 144, and a packing 148 is disposed on the end side thereof.
- the packings 146 and 148 keep the air channel 144 airtight.
- the adjustment port 32A can communicate with the fourth pressure chamber 44 via the air channel 144, the channel 143, and the through-hole 139. That is, in this embodiment, the through-hole 139, the channel 143, and the air channel 144 constitute an exhaust path.
- the through-hole 139 is closed by the packings 141 and 142, and high-pressure fluid in the fourth pressure chamber 44 is not discharged.
- the booster piston 22A moves to an end-side position, the detection pin 137 is pushed toward the end side, so that the packings 141 and 142 are disposed on the end side of the channel 143.
- the adjustment port 32A communicates with the fourth pressure chamber 44.
- the fluid pressure cylinder 10A of this embodiment configured as above is operated by a drive device 120A illustrated in FIGS. 11A and 11B .
- the drive device 120A includes a fourth check valve 86, a throttle valve 88, a switching valve 102, a high-pressure-air supply source 104, an exhaust port 106, and a fifth check valve 108.
- the drive device 120A is configured to supply high-pressure air to the first pressure chamber 38 in the working cylinder chamber 14a during the working process.
- the drive device 120A is configured to supply high-pressure air to the fourth pressure chamber 44 while supplying part of air accumulated in the first pressure chamber 38 to the second pressure chamber 40 during the return process.
- the switching valve 102 is, for example, a 5-port, 2-position valve including a first port 102a to a fifth port 102e and is switchable between a first position (see FIG. 11A ) and a second position (see FIG. 11B ).
- the first port 102a is connected to the head-side port 28A by pipes.
- the second port 102b is connected to the adjustment port 32A and the downstream side of the fifth check valve 108 by pipes.
- the third port 102c is connected to the exhaust port 106 by pipes.
- the fourth port 102d is connected to the high-pressure-air supply source 104 by pipes.
- the fifth port 102e is connected to the exhaust port 106 via the throttle valve 88 and to the end-side port 30A and the upstream side of the fifth check valve 108 via the fourth check valve 86 by pipes.
- the switching valve 102 when the switching valve 102 is in the first position, the first port 102a is connected to the fourth port 102d, and the second port 102b is connected to the third port 102c.
- the switching valve 102 when the switching valve 102 is in the second position, the first port 102a is connected to the fifth port 102e, and the second port 102b is connected to the fourth port 102d.
- the switching valve 102 is switched between the first position and the second position by pilot pressure from the high-pressure-air supply source 104 or by a solenoid valve.
- the fourth check valve 86 allows air to flow from the head-side port 28A toward the end-side port 30A and blocks air flowing from the end-side port 30A toward the head-side port 28A.
- the fifth check valve 108 blocks high-pressure air flowing from the second port 102b toward the end-side port 30A.
- the fluid pressure cylinder 10A according to this embodiment and the drive device 120A are configured as above. Next, the effects and operations thereof will be described.
- the switching valve 102 of the drive device 120A is set in the first position as illustrated in FIG. 11A .
- High-pressure air is supplied from the high-pressure-air supply source 104 to the head-side port 28A via the first port 102a of the switching valve 102.
- High-pressure air does not flow toward the fourth check valve 86 since the fourth check valve 86 is connected to the fifth port 102e.
- the second pressure chamber 40 is connected to the exhaust port 106 via the end-side port 30A and the fifth check valve 108.
- the adjustment port 32A is also connected to the exhaust port 106.
- high-pressure air of an amount equal to the volume of the first pressure chamber 38 is supplied from the high-pressure-air supply source 104 (see FIG. 11A ) to the fluid pressure cylinder 10A.
- the pressure of the high-pressure air stored in the third pressure chamber 42 and the pressure in the fourth pressure chamber 44 are kept constant.
- air in the second pressure chamber 40 is discharged from the second pressure chamber 40 as the working piston 20 moves. In this case, the air in the second pressure chamber 40 is discharged from the exhaust port 106 through the end-side port 30A and the fifth check valve 108 as illustrated in FIG. 11A .
- the communication switching pin 35a of the communication switching valve 35A is pushed toward the head side, while the detection pin 37a of the exhaust switching valve 37A is pushed toward the end side.
- the closing part 35c of the communication switching pin 35a is inserted into the through-hole 122 and closes the through-hole 122. This blocks the communication of high-pressure air between the third pressure chamber 42 and the fourth pressure chamber 44.
- the packings 141 and 142 that have sealed the gap between the detection pin 37a and the through-hole 139 are separated from the channel 143, whereby the adjustment port 32A communicates with the fourth pressure chamber 44.
- the high-pressure air stored in the fourth pressure chamber 44 is discharged from the exhaust port 106. That is, the internal pressure in the fourth pressure chamber 44 drops while the high-pressure air is kept in the third pressure chamber 42.
- thrust force corresponding to a difference between the internal pressure in the fourth pressure chamber 44 and the internal pressure in the third pressure chamber 42 acts on the booster piston 22A.
- the thrust force in the fluid pressure cylinder 10A increases near the stroke end. In this manner, in the fluid pressure cylinder 10A, the thrust force is increased by the discharge of the high-pressure air in the fourth pressure chamber 44 while the communication switching valve 35A and the exhaust switching valve 37A are being actuated.
- the switching valve 102 of the drive device 120A is set in the second position as illustrated in FIG. 11B .
- High-pressure air is supplied from the high-pressure-air supply source 104 to the adjustment port 32A via the second port 102b of the switching valve 102.
- the first port 102a of the switching valve 102 is connected to the fifth port 102e, and thereby the head-side port 28A is connected to the end-side port 30A via the fourth check valve 86.
- the head-side port 28A is also connected to the exhaust port 106 via the throttle valve 88.
- part of the air stored in the first pressure chamber 38 is supplied to the second pressure chamber 40 via the route with the fourth check valve 86.
- the remaining part of the air stored in the first pressure chamber 38 is discharged from the exhaust port 106.
- high-pressure air is supplied from the high-pressure-air supply source 104 to the adjustment port 32A of the fluid pressure cylinder 10A.
- the high-pressure air supplied to the adjustment port 32A flows into the fourth pressure chamber 44.
- high-pressure air discharged during the boosting process is supplemented.
- the amount of high-pressure air supplemented at this moment is small compared with the volume of the high-pressure air required for the stroke movement of the working piston, only a small addition of high-pressure air is required.
- part of the high-pressure air discharged from the first pressure chamber 38 flows into the second pressure chamber 40.
- the air inside the first pressure chamber 38 continues to be discharged, a difference between the pressure in the second pressure chamber 40 and the pressure in the first pressure chamber 38 increases, and the working piston 20 starts moving toward the head side. Subsequently, the working piston 20 and the booster piston 22A return to the start-of-stroke position, and the return process is completed.
- the second pressure chamber 40 does not need to be supplied with high-pressure air since air required for the working piston 20 to return to the start-of-stroke position is supplied from the first pressure chamber 38.
- the fluid pressure cylinder 10A according to this embodiment produces the following advantageous effects.
- a boost switching mechanism 33A includes the communication switching valve 35A provided in the booster piston 22A and the exhaust switching valve 37A provided in the rod cover 48A.
- the fluid pressure cylinder 10A can increase the thrust force at the stroke end without any complicated locking mechanisms. Moreover, since a mechanical locking mechanism for connecting the piston and the piston rod is not required, nonconformity is less likely to occur due to an axial impact, resulting in excellent reliability.
- the diameter of the booster piston 22A can be made larger than the diameter of the working piston 20. Due to the booster piston 22A with an increased diameter, it is possible to reduce the diameter of the working piston 20 while maintaining the thrust force at the stroke end, and thus it is possible to further reduce the consumption of high-pressure air.
- the drive devices 120 and 120A of the fluid pressure cylinders 10 and 10A are disposed outside the fluid pressure cylinders 10 and 10A.
- the present invention is not limited in particular to this. Part or all of the members constituting the drive devices 120 and 120A may be included inside the cylinder body 12.
Description
- The present invention relates to a fluid pressure cylinder (hydraulic cylinder).
- There are cases in which, in working machines such as clamping devices and locking devices, a large driving force is required in the latter half of a working process while such a large driving force is not required in the first half of the working process. For dealing with such cases, there has been proposed a fluid pressure cylinder with a booster mechanism, which increases thrust force in the latter half of a forward stroke of a piston rod by using the booster mechanism, as a fluid pressure cylinder used in such working machines.
- For example, a fluid pressure cylinder described in
Japanese Laid-Open Patent Publication No. 2018-017269 - An actuator assembly known from
EP 2 314 884 A2 comprises a first cylinder housing a first piston and a second cylinder housing a second piston. The first and second pistons are coupled together, and the first cylinder is provided with a selectively closable conduit enabling fluid to flow from one side of the first piston to the other and a flow restrictor enabling the rate of fluid flow through the conduit to be selectively controlled. The flow restrictor may serve to selectively close the conduit. There may be a second selectively closable conduit provided in parallel with the first conduit over all or part of the length of the first conduit. The second conduit may have a larger flow capacity than the first conduit. The actuator may be operated by compressed air or gas, or another suitable fluid, for example a liquid such as oil or water. The actuator assembly may be provided with a control means to automatically control its operation. - Document
US 2017/0108014 A1 discloses a hydraulic drive comprising a working cylinder and a travel cylinder which is mechanically connected to the working cylinder. The working cylinder and the travel cylinder each comprise an upper and a lower cylinder chamber, and all four cylinder chambers of the working and travel cylinder are connected to one another in a suitable manner in a closed pressure circuit which is filled and prestressed with a hydraulic fluid. A rotational speed-variable hydraulic machine with a first and second pressure connection is arranged in the pressure circuit in order to conduct the hydraulic fluid between the individual cylinder chambers of the working and travel cylinder during the operation of the hydraulic drive. At least one first and second distributing valve are arranged in the pressure circuit such that the respective valve switch positions which are suitable for the different operating phases of the hydraulic drive together with the suitably driven hydraulic machine allow a common movement of the work and travel cylinder in one or the other piston movement direction. For this purpose, preferably only the first and the second distributing valve are arranged in the pressure circuit. - To reduce energy consumption, a further reduction in the consumption of working fluid is required for the fluid pressure cylinder with the booster mechanism.
- The present invention has been devised taking into consideration the aforementioned problem, and has the object of providing a fluid pressure cylinder with a booster function, which is capable of reducing the consumption of working fluid without complicated structures.
- According to the present invention there is provided a fluid pressure cylinder comprising the features of
claim 1 or 3. - Preferred embodiments of the invention are defined in the dependent claims.
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FIG. 1 is a cross-sectional view of a fluid pressure cylinder according to a first embodiment, including a partially enlarged cross-sectional view of athird check valve 56; -
FIG. 2 is a side view of the fluid pressure cylinder inFIG. 1 viewed from an end side; -
FIG. 3A is an enlarged cross-sectional view of a part adjacent to a partition wall of the fluid pressure cylinder inFIG. 1 , andFIG. 3B is an enlarged cross-sectional view of a state in which a working piston is disposed adjacent to the partition wall inFIG. 3A ; -
FIG. 4A is a fluid circuit diagram illustrating a connection state of the fluid pressure cylinder according to the embodiment during a working process, andFIG. 4B is a fluid circuit diagram illustrating a connection state of the fluid pressure cylinder inFIG. 4A during a return process; -
FIG. 5 is a cross-sectional view of the fluid pressure cylinder inFIG. 1 during the working process; -
FIG. 6 is a cross-sectional view of the fluid pressure cylinder inFIG. 1 during a boosting process; -
FIG. 7 is a cross-sectional view (View 1) of the fluid pressure cylinder inFIG. 1 during the return process; -
FIG. 8 is a cross-sectional view (View 2) of the fluid pressure cylinder inFIG. 1 during the return process; -
FIG. 9A is a plan view of a fluid pressure cylinder according to a second embodiment, andFIG. 9B is a side view of the fluid pressure cylinder inFIG. 9A ; -
FIG. 10 is a cross-sectional view of the fluid pressure cylinder inFIG. 9A at a start-of-stroke position; -
FIG. 11A is a fluid circuit diagram of a drive device of the fluid pressure cylinder inFIG. 9A illustrating a connection state when a switching valve is in a first position, andFIG. 11B is a fluid circuit diagram illustrating a connection state when the switching valve of the drive device inFIG. 11A is in a second position; and -
FIG. 12 is a cross-sectional view of the fluid pressure cylinder inFIG. 9A during the boosting process. - Preferred embodiments of the present invention will be described in detail below with reference to the accompanying drawings. The ratio of the dimensions in the drawings may be exaggerated and differ from the actual ratio for convenience of explanation. In this description, a direction toward an end-of-stroke position is referred to as "end direction" or "end side", and a direction where a start-of-stroke position is located is referred to as "head direction" or "head side". Moreover, in this description, "air" refers to working fluid in gaseous form and is not limited in particular to air.
- As illustrated in
FIGS. 4A and 4B , afluid pressure cylinder 10 according to this embodiment includes acylinder body 12 and adrive device 120. - As illustrated in
FIG. 1 , thefluid pressure cylinder 10 includes thecylinder body 12 extending in the axial direction. Thecylinder body 12 may have a rectangular shape as illustrated inFIG. 2 and is composed of, for example, a metal material such as aluminum alloy. - As illustrated in
FIG. 1 , thecylinder body 12 contains, formed therein, acircular slide hole 12a (cylinder chamber) extending in the axial direction. Thecylinder body 12 includes a head-side body portion 14 disposed on the head side, an end-side body portion 16 disposed on the end side, and apartition wall 26 disposed between the head-side body portion 14 and the end-side body portion 16. As illustrated inFIG. 2 , the head-side body portion 14, thepartition wall 26, and the end-side body portion 16 are fastened together in the axial direction by connecting rods orbolts 16b. - As illustrated in
FIG. 1 , the head-side body portion 14 contains, formed therein, a circularworking cylinder chamber 14a, and the end-side body portion 16 contains, formed therein, a circularbooster cylinder chamber 16a. The workingcylinder chamber 14a and thebooster cylinder chamber 16a have an identical inner diameter and constitute theslide hole 12a of thecylinder body 12. The workingcylinder chamber 14a and thebooster cylinder chamber 16a are separated by thepartition wall 26. - A working
piston 20 is disposed in the workingcylinder chamber 14a, and abooster piston 22 is disposed in thebooster cylinder chamber 16a. The workingpiston 20 and thebooster piston 22 are connected to apiston rod 18 extending toward the end side and penetrating through thepartition wall 26 and thecylinder body 12. - The head-
side body portion 14 is provided with a head-side port 28, ahead cover 46, and the workingpiston 20. Thehead cover 46 is attached to the head-side end of the workingcylinder chamber 14a, and seals the head side of the workingcylinder chamber 14a. - The head-
side port 28 is provided adjacent to thehead cover 46. The head-side port 28 penetrates through the head-side body portion 14. The head-side port 28 communicates with the workingcylinder chamber 14a (first pressure chamber 38) via anopening 28a provided adjacent to the head-side end of the workingcylinder chamber 14a. - The working
piston 20 is accommodated inside the workingcylinder chamber 14a so as to be slidable in the axial direction. An annularpacking receiving groove 21a is formed in the outer circumferential surface of the workingpiston 20, and a packing 21 is disposed into thepacking receiving groove 21a. The packing 21 comes into close contact with the inner circumferential surface of the workingcylinder chamber 14a while elastically deforming, and thereby airtightly partitions the workingcylinder chamber 14a into thefirst pressure chamber 38 and asecond pressure chamber 40. Thefirst pressure chamber 38 is an empty chamber formed between the workingpiston 20 and thehead cover 46 and is located on the head side of the workingpiston 20. Thesecond pressure chamber 40 is an empty chamber formed between the workingpiston 20 and thepartition wall 26 and is located on the end side of the workingpiston 20. Thefirst pressure chamber 38 communicates with the head-side port 28 via theopening 28a. - The working
piston 20 is connected to thepiston rod 18 at a head-side connection portion 18a of thepiston rod 18 and displaceable integrally with thepiston rod 18. - The end-
side body portion 16 is provided with thebooster piston 22, arod cover 48, an end-side port 30, and anauxiliary path 76. - The
booster piston 22 is disposed inside thebooster cylinder chamber 16a in the end-side body portion 16 so as to be slidable in the axial direction. An annularpacking receiving groove 23a and an annularmagnet receiving groove 24a are formed in the outer circumferential surface of thebooster piston 22. Anannular packing 23 composed of an elastic material such as rubber is mounted into thepacking receiving groove 23a. A circular ring-shapedmagnet 24 is mounted into themagnet receiving groove 24a. A wear ring (not illustrated) is attached to an outer circumferential portion of themagnet 24. - The
booster piston 22 airtightly partitions thebooster cylinder chamber 16a into athird pressure chamber 42 and afourth pressure chamber 44 via the packing 23. Thethird pressure chamber 42 is an empty chamber formed between thebooster piston 22 and thepartition wall 26 and is located on the head side of thebooster piston 22. Thefourth pressure chamber 44 is an empty chamber formed between thebooster piston 22 and therod cover 48 and is located on the end side of thebooster piston 22. Thefourth pressure chamber 44 communicates with the end-side port 30. - An annular
damper receiving groove 25a is formed in the head-side end face of thebooster piston 22, and adamper 25 is mounted into thedamper receiving groove 25a. Thedamper 25 is composed of an elastic material such as rubber and is configured to prevent collision of thebooster piston 22 with thepartition wall 26. Thebooster piston 22 is connected to apiston attachment portion 18b located in the midsection of thepiston rod 18 and is displaceable in the axial direction integrally with thepiston rod 18. - The
rod cover 48 is attached to an end-side part of thebooster cylinder chamber 16a. Therod cover 48 has a disk shape and includes an annularpacking receiving groove 48d formed in an outer circumferential part thereof. A circular ring-shapedpacking 48c is mounted into thepacking receiving groove 48d. Thepacking 48c airtightly seals thepacking receiving groove 48d. - The
rod cover 48 has aninsertion hole 48a in the vicinity of the radial center. Theinsertion hole 48a extends in the axial direction, and thepiston rod 18 passes therethrough. Arod packing 48b is disposed in theinsertion hole 48a to prevent leakage of air along thepiston rod 18. An annulardamper receiving groove 47a is formed in the head-side end face of therod cover 48, and adamper 47 is mounted into thedamper receiving groove 47a. Thedamper 47 is composed of an elastic member having a circular ring shape. Thedamper 47 protrudes toward the interior of thebooster cylinder chamber 16a to prevent collision of therod cover 48 with thebooster piston 22. - A retaining
clip 49 is attached to an end-side part of therod cover 48 to secure therod cover 48. The retainingclip 49 is a plate member engaged into an engaginggroove 49a formed in the end-side body portion 16 along the inner circumferential surface of the end-side body portion 16. The retainingclip 49 is an annular plate member having a gap at a circumferential position. The retaining clip is engaged into the engaginggroove 49a by the elastic restoring force and is in contact with the end-side end face of therod cover 48, thereby preventing therod cover 48 from coming off. - The end-
side port 30 is formed in the end-side body portion 16 adjacent to the end-side end. The end-side port 30 penetrates through the end-side body portion 16 from the outer circumference to thebooster cylinder chamber 16a and communicates with thefourth pressure chamber 44 at an end-side end part of thebooster cylinder chamber 16a. - The
auxiliary path 76 is a flow path formed inside the end-side body portion 16 and extends in the axial direction. A first end of theauxiliary path 76 communicates with the end-side port 30, and a second end thereof communicates with an adjustment port 32 (described below) in thepartition wall 26. - A
third check valve 56 is disposed at a position on theauxiliary path 76. Thethird check valve 56 includes ahollow portion 56a having a larger diameter than theauxiliary path 76 and avalve element 56b inserted into thehollow portion 56a. Thevalve element 56b is a cup-shaped member having a cylindrical shape with a bottom, and the bottom 56c is disposed downstream in an airflow that is to be blocked. The bottom 56c of thevalve element 56b includes anannular protrusion 56d which is brought into contact with an end face of thehollow portion 56a to thereby block theauxiliary path 76 communicating with thehollow portion 56a. - A
cutout portion 56e is formed in a side part of thevalve element 56b to allow air to pass. When air flows from the bottom 56c side into the hollow portion, theannular protrusion 56d of thevalve element 56b is configured to be separated from the end face of thehollow portion 56a to thereby pass the air via thecutout portion 56e. When air flows in the opposite direction, the bottom 56c of thevalve element 56b is configured to receive the pressure of the air to thereby bring theannular protrusion 56d into contact with the end face of thehollow portion 56a and block theauxiliary path 76, so that the airflow is stopped. - To cause the
third check valve 56 to operate smoothly, a biasingmember 56f such as a spring may be disposed inside thehollow portion 56a to bias theannular protrusion 56d of thevalve element 56b toward the end face of thehollow portion 56a. Note that afirst check valve 52 and asecond check valve 54 described below have structures similar to that of thethird check valve 56. - As illustrated in
FIG. 3A , thepartition wall 26 includes a plate-shapedbody 60. Thebody 60 includes afirst connection part 63 protruding toward the head side so as to be inserted into the workingcylinder chamber 14a and asecond connection part 64 protruding toward the end side so as to be inserted into thebooster cylinder chamber 16a. Thefirst connection part 63 has a circular cylindrical shape having an outer diameter substantially equal to the inner diameter of the workingcylinder chamber 14a. Apacking 63a is attached to an outer circumferential part of thefirst connection part 63. Thesecond connection part 64 has a circular cylindrical shape having an outer diameter substantially equal to the inner diameter of thebooster cylinder chamber 16a. Apacking 64a is attached to an outer circumferential part of thesecond connection part 64. Thepacking 63a seals the gap between the workingcylinder chamber 14a and thefirst connection part 63. Thepacking 64a seals the gap between thebooster cylinder chamber 16a and thesecond connection part 64. - The
partition wall 26 includes a through-hole part 61 in the vicinity of the radial center. The through-hole part 61 extends in the axial direction, and thepiston rod 18 passes therethrough. A packing 62 is disposed in the through-hole part 61 to prevent leakage of air along thepiston rod 18. - The
partition wall 26 further includes acommunication path 34, acommunication switching valve 35 disposed in thecommunication path 34, anexhaust path 36, and anexhaust switching valve 37 disposed in theexhaust path 36, which form aboost switching mechanism 33. - The
communication path 34 is a flow path that allows air to flow between thesecond pressure chamber 40 and thethird pressure chamber 42. Thecommunication path 34 includes a through-hole 65 penetrating through thepartition wall 26 in the axial direction, aninner channel 35e of acommunication switching pin 35a inserted into the through-hole 65, and ahole 66b of astopper 66. - The through-
hole 65 penetrates through thepartition wall 26 in the axial direction and includes a large-diameter part 65a disposed on the head side, a small-diameter part 65b disposed in the middle in the axial direction, and astopper insertion hole 65c disposed on the end side. The large-diameter part 65a and thestopper insertion hole 65c have larger inner diameters than the small-diameter part 65b. Thecommunication switching pin 35a is disposed inside the large-diameter part 65a and the small-diameter part 65b. Thestopper 66 is inserted into thestopper insertion hole 65c. Thestopper 66 is connected to an end-side part of thecommunication switching pin 35a of thecommunication switching valve 35 and is displaced integrally with thecommunication switching pin 35a. Movement of thecommunication switching pin 35a toward the head side is restricted when thestopper 66 stops inside thestopper insertion hole 65c. - The
communication switching valve 35 includes thecommunication switching pin 35a. Thecommunication switching pin 35a includes aclosing part 35c disposed on the head side and arod part 35d extending in the axial direction toward the end side. Therod part 35d has a diameter substantially equal to the inner diameter of the small-diameter part 65b of the through-hole 65, and the rod part is inserted into the small-diameter part 65b so as to be slidable in the axial direction. The closingpart 35c has a diameter substantially equal to the inner diameter of the large-diameter part 65a of the through-hole 65 so as to be insertable into the large-diameter part 65a. A ring-shapedpacking 35b is attached to an outer circumferential part of theclosing part 35c. When theclosing part 35c is pushed into the large-diameter part 65a, thepacking 35b comes into close contact with the large-diameter part 65a and thereby seals thecommunication path 34. - A biasing
member 35f is attached to the end side of theclosing part 35c of thecommunication switching pin 35a. The biasingmember 35f is formed by, for example, a spring, and disposed in the gap between the large-diameter part 65a and thecommunication switching pin 35a. The biasingmember 35f biases thecommunication switching pin 35a toward the head side such that theclosing part 35c is separated from the through-hole 65 and protrudes into thesecond pressure chamber 40. That is, thecommunication switching valve 35 does not block thecommunication path 34 in a state that thecommunication switching pin 35a is not pushed, by the workingpiston 20, toward the end side. - The
exhaust path 36 has an opening on an end face of thepartition wall 26 on thefirst connection part 63 side. Theexhaust path 36 includes a detection-pinaccommodating hole 67 extending in the axial direction and a connectingchannel 71 communicating with both the detection-pinaccommodating hole 67 and theadjustment port 32. The detection-pinaccommodating hole 67 includes a large-diameter part 67a disposed on the head side, a small-diameter part 67b disposed on the end side of the large-diameter part 67a, and astopper insertion hole 67c. Astopper 68 is inserted into thestopper insertion hole 67c. Thestopper 68 is connected to adetection pin 37a and is displaced integrally with thedetection pin 37a. The moving range of thedetection pin 37a toward the head side is limited when thestopper 68 stops at the end-side end of the small-diameter part 67b. - The connecting
channel 71 communicates with the detection-pinaccommodating hole 67 at anopening part 71a formed in a side part of the small-diameter part 67b. The diameter of the small-diameter part 67b is increased in a predetermined region around theopening part 71a, so that a gap is left between the small-diameter part 67b and theexhaust switching valve 37. - The
first check valve 52, which allows air to flow only in a direction from theopening part 71a toward theadjustment port 32, is disposed in the connectingchannel 71. Thefirst check valve 52 is disposed in a direction so as to allow air from thesecond pressure chamber 40 to be discharged. - The
exhaust switching valve 37 includes thedetection pin 37a. Thedetection pin 37a includes apin body part 37b having a circular cylindrical shape extending in the axial direction and aflange part 37c extending radially outward from the head-side end of thepin body part 37b. Theflange part 37c has a diameter slightly smaller than the inner diameter of the large-diameter part 67a and is formed so as to be insertable into the large-diameter part 67a. A biasingmember 37f formed by, for example, a spring is disposed in the large-diameter part 67a. The biasingmember 37f is in contact with theflange part 37c and biases thedetection pin 37a toward the head side, so that theflange part 37c protrudes into thesecond pressure chamber 40. - The
pin body part 37b has a diameter slightly smaller than the inner diameter of the small-diameter part 67b and is configured to be slidable in the axial direction along the small-diameter part 67b. Apacking 37d and apacking 37e are disposed on an outer circumferential part of thepin body part 37b at a distance from each other in the axial direction. In a state that thedetection pin 37a is not pushed by the workingpiston 20, thepacking 37d and thepacking 37e are placed at positions where the packings are in close contact with the small-diameter part 67b to thereby block the communication between the detection-pinaccommodating hole 67 and the connectingchannel 71. That is, theexhaust switching valve 37 blocks theexhaust path 36 in the state that theexhaust switching valve 37 is not pushed by the workingpiston 20. - A
supplementary channel 78 and thesecond check valve 54 are provided in the head-side body portion 14 adjacent to theadjustment port 32. Thesupplementary channel 78 communicates with theadjustment port 32 and thesecond pressure chamber 40. Thesecond check valve 54 is disposed in thesupplementary channel 78. A first end of thesecond check valve 54 communicates with theadjustment port 32 via thesupplementary channel 78. A second end of thesecond check valve 54 communicates with thesecond pressure chamber 40 via thesupplementary channel 78. Thesecond check valve 54 allows air to flow only in a direction from theadjustment port 32 toward thesecond pressure chamber 40 and blocks flow of air in the opposite direction. That is, thesecond check valve 54 allows air for supplement to thesecond pressure chamber 40 to flow and blocks air flowing in the opposite direction. - The
fluid pressure cylinder 10 of this embodiment is configured as above and operated by thedrive device 120 as illustrated inFIG. 4A . - The
drive device 120 includes afourth check valve 86, athrottle valve 88, a switchingvalve 102, a high-pressure-air supply source (high-pressure-fluid supply source) 104, and anexhaust port 106. Thedrive device 120 is configured to supply high-pressure air to thefirst pressure chamber 38 in the workingcylinder chamber 14a during the working process. Moreover, as illustrated inFIG. 4B , thedrive device 120 is configured to supply high-pressure air to thesecond pressure chamber 40 while supplying part of air accumulated in thefirst pressure chamber 38 to thefourth pressure chamber 44 during the return process. - The switching
valve 102 is, for example, a 5-port, 2-position valve including afirst port 102a to afifth port 102e and is switchable between a first position (seeFIG. 4A ) and a second position (seeFIG. 4B ). As illustrated inFIGS. 4A and 4B , thefirst port 102a is connected to the head-side port 28 by pipes. Thesecond port 102b is connected to theadjustment port 32 by pipes. Thethird port 102c is connected to theexhaust port 106 by pipes. Thefourth port 102d is connected to the high-pressure-air supply source 104 by pipes. Thefifth port 102e is connected to theexhaust port 106 via thethrottle valve 88 and to the end-side port 30 via thefourth check valve 86 by pipes. - As illustrated in
FIG. 4A , when the switchingvalve 102 is in the first position, thefirst port 102a is connected to thefourth port 102d, and thesecond port 102b is connected to thethird port 102c. - Moreover, as illustrated in
FIG. 4B , when the switchingvalve 102 is in the second position, thefirst port 102a is connected to thefifth port 102e, and thesecond port 102b is connected to thefourth port 102d. The switchingvalve 102 is switched between the first position and the second position by pilot pressure from the high-pressure-air supply source 104 or by a solenoid valve. - When the switching
valve 102 is in the second position, thefourth check valve 86 allows air to flow from the head-side port 28 to the end-side port 30 and blocks air flowing from the end-side port 30 toward the head-side port 28. - The
throttle valve 88, which is an adjustable throttle valve of which path area can be changed to adjust the exhaust flow rate, limits the amount of air discharged from thefirst pressure chamber 38 through theexhaust port 106. - An air tank may be disposed at a position along a pipe connecting the
fourth check valve 86 and thefourth pressure chamber 44 to thereby accumulate air supplied from the head-side port 28 to the end-side port 30 during the return process. The air tank can accumulate air sufficient to fill thefourth pressure chamber 44 during the return operation, resulting in a stable return operation. In this case, the volume of the air tank may be set to, for example, about half the maximum volume of thefirst pressure chamber 38. The air tank is unnecessary in a case where the pipes have sufficient volume. - The
fluid pressure cylinder 10 and thedrive device 120 are configured as above. Next, the effects and operations thereof will be described. - Before the
fluid pressure cylinder 10 starts to be used, during a startup process, thesecond pressure chamber 40 and thethird pressure chamber 42 are filled with high-pressure air. The high-pressure air refers to air at a pressure higher than atmospheric pressure. Here, thefluid pressure cylinder 10 is set in the start-of-stroke position as illustrated inFIG. 1 . Moreover, the switchingvalve 102 of thedrive device 120 is in the second position (seeFIG. 4B ). The high-pressure-air supply source 104 is thus connected to theadjustment port 32. As illustrated inFIG. 4B , high-pressure air is introduced from the high-pressure-air supply source 104 into thesecond pressure chamber 40 via thesecond check valve 54. Moreover, the high-pressure air introduced into thesecond pressure chamber 40 is also introduced into thethird pressure chamber 42 via thecommunication path 34. In this manner, thesecond pressure chamber 40 and thethird pressure chamber 42 are filled with high-pressure air. The startup process may be performed only once before the first stroke of thefluid pressure cylinder 10. - During the working process of the
fluid pressure cylinder 10, the switchingvalve 102 of thedrive device 120 is set in the first position as illustrated inFIG. 4A . High-pressure air is supplied from the high-pressure-air supply source 104 to the head-side port 28 via thefirst port 102a of the switchingvalve 102. High-pressure air does not flow toward thefourth check valve 86 since thefourth check valve 86 is connected to thefifth port 102e. Thefourth pressure chamber 44 is connected to theexhaust port 106 via thethird check valve 56, theadjustment port 32, and thesecond port 102b. - As illustrated in
FIG. 5 , during the working process, high-pressure air from the high-pressure-air supply source 104 flows into thefirst pressure chamber 38 as indicated by an arrow B. Force exerted on the working piston by the high-pressure air in thesecond pressure chamber 40 and force exerted on thebooster piston 22 by the high-pressure air that fills thethird pressure chamber 42 are equal in magnitude and balanced in the opposite direction. Thus, the forces do not contribute to thrust force. As a result, thrust force corresponding to a difference between the pressure in thefirst pressure chamber 38 adjoining the workingpiston 20 and the pressure in thefourth pressure chamber 44 adjoining thebooster piston 22 acts on thepiston rod 18, and thepiston rod 18 moves toward the end side. - As the working
piston 20 moves, high-pressure air of an amount equal to the volume of thefirst pressure chamber 38 is supplied from the high-pressure-air supply source 104 (seeFIG. 4A ) to thefluid pressure cylinder 10. As the workingpiston 20 and thebooster piston 22 move, the high-pressure air inside thesecond pressure chamber 40 moves to thethird pressure chamber 42 via thecommunication path 34. During the working process, the pressure of the high-pressure air stored in thesecond pressure chamber 40 and the pressure of the high-pressure air stored in thethird pressure chamber 42 are kept constant. Moreover, air in thefourth pressure chamber 44 is discharged from thefourth pressure chamber 44 as thebooster piston 22 moves. In this case, the air in thefourth pressure chamber 44 passes through theadjustment port 32 via thethird check valve 56 and theauxiliary path 76, and is discharged from theexhaust port 106 through thesecond port 102b of the switchingvalve 102 as illustrated inFIG. 4A . - As illustrated in
FIG. 6 , as the workingpiston 20 moves, thecommunication switching pin 35a (seeFIG. 3B ) of thecommunication switching valve 35 is pushed toward the end side, and thedetection pin 37a (seeFIG. 3B ) of theexhaust switching valve 37 is also pushed toward the end side. - As a result, as illustrated in
FIG. 3B , the closingpart 35c of thecommunication switching pin 35a is inserted into the large-diameter part 65a of the through-hole 65. The packing 35b on theclosing part 35c seals the gap between the large-diameter part 65a and theclosing part 35c, thereby blocking thecommunication path 34. That is, thecommunication switching valve 35 blocks the communication of air between thesecond pressure chamber 40 and thethird pressure chamber 42 via thecommunication path 34. - Moreover, as the
detection pin 37a of theexhaust switching valve 37 is displaced toward the end side, thepacking 37d that has sealed the gap between thedetection pin 37a and the detection-pinaccommodating hole 67 moves to the recessedopening part 71a. This movement opens theexhaust path 36, and theadjustment port 32 and thesecond pressure chamber 40 communicate with each other via theexhaust path 36. The high-pressure air stored in thesecond pressure chamber 40 is discharged from theexhaust port 106 via thefirst check valve 52 and theadjustment port 32. As a result, the internal pressure in thesecond pressure chamber 40 drops, and thrust force corresponding to a difference between the internal pressure in thesecond pressure chamber 40 and the internal pressure in thefirst pressure chamber 38 acts on the workingpiston 20. - Moreover, thrust force corresponding to a difference between the pressure of the high-pressure air stored in the
third pressure chamber 42 and the pressure in thefourth pressure chamber 44 acts on thebooster piston 22. In this manner, thefluid pressure cylinder 10 can increase the thrust force near the stroke end. In thefluid pressure cylinder 10, the thrust force is increased by the discharge of the high-pressure air in thesecond pressure chamber 40 while thecommunication switching valve 35 and theexhaust switching valve 37 are being actuated. - During the return process of the
fluid pressure cylinder 10, the switchingvalve 102 of thedrive device 120 is set in the second position as illustrated inFIG. 4B . High-pressure air is supplied from the high-pressure-air supply source 104 to theadjustment port 32 via thesecond port 102b of the switchingvalve 102. Thefirst port 102a of the switchingvalve 102 is connected to thefifth port 102e, and thereby the head-side port 28 is connected to the end-side port 30 via thefourth check valve 86. The head-side port 28 is also connected to theexhaust port 106 via thethrottle valve 88. As a result, part of the air stored in thefirst pressure chamber 38 is supplied to thefourth pressure chamber 44 via the route with thefourth check valve 86. The remaining part of the air stored in thefirst pressure chamber 38 is discharged from theexhaust port 106. - As illustrated in
FIG. 7 , during the return process, high-pressure air from the high-pressure-air supply source 104 is supplied to theadjustment port 32 of thefluid pressure cylinder 10 as indicated by an arrow B. The high-pressure air supplied to theadjustment port 32 flows into thesecond pressure chamber 40 through thesupplementary channel 78 and thesecond check valve 54. The volume of the high-pressure air supplied to thesecond pressure chamber 40 is equal to the volume of the high-pressure air discharged from thesecond pressure chamber 40 during the boosting process. That is, high-pressure air required for the boosting process is supplemented during the return process. The amount of high-pressure air supplied at this moment is small compared with the volume of the high-pressure air required for movement of the workingpiston 20, and thus only a small addition of high-pressure air is required. - During the return process, the internal pressure in the
second pressure chamber 40 and the internal pressure in thethird pressure chamber 42 become equal to each other. Consequently, the force exerted on the workingpiston 20 by thesecond pressure chamber 40 and the force exerted on thebooster piston 22 by thethird pressure chamber 42 are balanced and canceled. - On the other hand, part of the high-pressure air discharged from the
first pressure chamber 38 flows into thefourth pressure chamber 44 as indicated by an arrow A. As the air inside thefirst pressure chamber 38 continues to be discharged, the difference between the pressure in thefourth pressure chamber 44 and the pressure in thefirst pressure chamber 38 increases, and the workingpiston 20, thebooster piston 22, and thepiston rod 18 start moving toward the head side. Along with this, thecommunication switching valve 35 returns to its original position, and thesecond pressure chamber 40 and thethird pressure chamber 42 communicate with each other through thecommunication path 34. Moreover, theexhaust switching valve 37 seals theexhaust path 36 and blocks the communication between theadjustment port 32 and thesecond pressure chamber 40. - Subsequently, as illustrated in
FIG. 8 , air in thefirst pressure chamber 38 continues to be discharged while air flows into thefourth pressure chamber 44, and the workingpiston 20 and thebooster piston 22 return to the start-of-stroke position. The return process is then completed. - The
fluid pressure cylinder 10 according to this embodiment produces the following advantageous effects. - In the
fluid pressure cylinder 10, thefluid pressure cylinder 10 includes, as theboost switching mechanism 33, thecommunication path 34 communicating with thesecond pressure chamber 40 and thethird pressure chamber 42, theexhaust path 36 communicating with thesecond pressure chamber 40, thecommunication switching valve 35 configured to open thecommunication path 34 when the workingpiston 20 is located on the head side of a predetermined position and configured to close thecommunication path 34 when the workingpiston 20 moves to the end side of the predetermined position, and theexhaust switching valve 37 configured to close theexhaust path 36 when the workingpiston 20 is located on the head side of the predetermined position and configured to open theexhaust path 36 to discharge high-pressure fluid in thesecond pressure chamber 40 when the workingpiston 20 moves to the end side of the predetermined position. This causes thesecond pressure chamber 40 and thethird pressure chamber 42 to be separated near the stroke end and enables the high-pressure air in thesecond pressure chamber 40 to be discharged while the high-pressure air in thethird pressure chamber 42 is maintained. As a result, thrust force of thebooster piston 22 is added to the thrust force of the workingpiston 20, and it is thus possible to increase the thrust force in the latter half of the stroke. - In the
fluid pressure cylinder 10, thepartition wall 26 may include theadjustment port 32, and theexhaust path 36 may be configured to discharge the high-pressure fluid in thesecond pressure chamber 40 via theadjustment port 32. - In the
fluid pressure cylinder 10, theboost switching mechanism 33 may be configured such that theexhaust switching valve 37 opens theexhaust path 36 after thecommunication switching valve 35 closes thecommunication path 34. This prevents the outflow of high-pressure air from thethird pressure chamber 42 via thesecond pressure chamber 40, thereby reducing the consumption of high-pressure air. - In the
fluid pressure cylinder 10, thecommunication switching valve 35 may include thecommunication switching pin 35a including the first end that protrudes into thesecond pressure chamber 40 and the second end that is inserted into thecommunication path 34, and may be configured to block thecommunication path 34 when thecommunication switching pin 35a is pushed by the workingpiston 20 and displaced toward the end side. This enables thecommunication switching valve 35 to operate using the stroke movement of the workingpiston 20, thereby simplifying the device structure. - In the
fluid pressure cylinder 10, theexhaust switching valve 37 may include thedetection pin 37a including the first end that protrudes into thesecond pressure chamber 40 and sealing theexhaust path 36, and may be configured to unseal or open theexhaust path 36 when thedetection pin 37a is pushed by the workingpiston 20 and displaced toward the end side. This enables the air in thesecond pressure chamber 40 to be discharged via theexhaust path 36 using the stroke movement of the workingpiston 20, thereby simplifying the device structure. - In the
fluid pressure cylinder 10, theexhaust path 36 may be provided with thefirst check valve 52 allowing air to flow only in a direction from thesecond pressure chamber 40 toward theadjustment port 32 and blocking air flowing in the opposite direction. This prevents malfunctions of theexhaust switching valve 37 during the return process. - The
fluid pressure cylinder 10 may further includes thesupplementary channel 78 communicating with theadjustment port 32 and thesecond pressure chamber 40. Thesupplementary channel 78 may be provided with thesecond check valve 54 allowing air to flow only in a direction from theadjustment port 32 toward thesecond pressure chamber 40 and blocking air flowing in the opposite direction. Provision of thesecond check valve 54 prevents excessive inflow of high-pressure air into thesecond pressure chamber 40 during the return process. - The
fluid pressure cylinder 10 may further include theauxiliary path 76 communicating with thefourth pressure chamber 44 and theadjustment port 32. This enables the air in thefourth pressure chamber 44 to be discharged through theadjustment port 32 during the working process and the boosting process. - In the
fluid pressure cylinder 10, theauxiliary path 76 may be provided with thethird check valve 56 allowing air to flow only in a direction from thefourth pressure chamber 44 toward theadjustment port 32 and blocking air flowing in the opposite direction. This prevents high-pressure air from flowing into thefourth pressure chamber 44 when high-pressure air is supplied to theadjustment port 32 during the return process, thereby reducing the consumption of high-pressure air. - The
fluid pressure cylinder 10 may further include thedrive device 120 connected to thefirst pressure chamber 38, thesecond pressure chamber 40, and thefourth pressure chamber 44 of thefluid pressure cylinder 10. Thedrive device 120 may include the switchingvalve 102, the high-pressure-air supply source 104, theexhaust port 106, and thefourth check valve 86. When the switchingvalve 102 is in the first position, thefirst pressure chamber 38 may communicate with the high-pressure-air supply source 104, and thefourth pressure chamber 44 and the adjustment port 32 (boost switching mechanism 33) may communicate with theexhaust port 106. When the switchingvalve 102 is in the second position, thefirst pressure chamber 38 may communicate with thefourth pressure chamber 44 via thefourth check valve 86 and with theexhaust port 106, and thesecond pressure chamber 40 may communicate with the high-pressure-air supply source 104 via theadjustment port 32. This enables thefourth pressure chamber 44 to be supplied with the air accumulated in thefirst pressure chamber 38 during the return process, thereby reducing the consumption of high-pressure air. - The
fluid pressure cylinder 10 may further include thethrottle valve 88 disposed between thefirst pressure chamber 38 and theexhaust port 106. This allows the amount of air supplied to thefourth pressure chamber 44 to be appropriately adjusted. - As illustrated in
FIG. 9A , afluid pressure cylinder 10A according to this embodiment includes a head-side body portion 14A and an end-side body portion 16A. In this embodiment, high-pressure fluid is enclosed in the end-side body portion 16A. To further increase the thrust force at the stroke end, the size (width and height) of the end-side body portion 16A is made larger than the size of the head-side body portion 14A. - As illustrated in
FIG. 9B , the head-side body portion 14A and the end-side body portion 16A have rectangular cross-sections. The head-side body portion 14A and the end-side body portion 16A are fastened together in the axial direction by connecting rods or bolts. - As illustrated in
FIG. 10 , acylinder body 12A of thefluid pressure cylinder 10A includes the head-side body portion 14A and the end-side body portion 16A connected to each other in the axial direction via apartition wall 126. The head-side body portion 14A includes a head-side port 28A and an end-side port 30A. The end-side body portion 16A includes anadjustment port 32A adjacent to the end-side end. - A stored-
air exhaust port 162 is formed in a portion of thepartition wall 126 adjacent to the outer circumference in order to discharge high-pressure air enclosed in abooster cylinder chamber 116a. The stored-air exhaust port 162 communicates with athird pressure chamber 42 via a regulatingvalve 160. The stored-air exhaust port 162 is used to discharge high-pressure air stored inside thebooster cylinder chamber 116a during, for example, the maintenance of thefluid pressure cylinder 10A and to introduce high-pressure air into thebooster cylinder chamber 116a at startup. - An insertion hole 126c into which a
piston rod 18A is slidably inserted is formed in a central part of thepartition wall 126. A packing 118 is disposed in the insertion hole 126c to prevent leakage of fluid in the axial direction. Thepartition wall 126 includes a head-side connection part 126a protruding toward the head side and inserted into a workingcylinder chamber 14a. Thepartition wall 126 further includes an end-side connection part 126b protruding toward the end side and inserted into thebooster cylinder chamber 116a. Anannular cushion member 124 is attached to the end-side connection part 126b to prevent the end-side connection part 126b from colliding with abooster piston 22A. - The end-
side body portion 16A includes abody part 116. Thebooster cylinder chamber 116a, which is a circular cavity, is formed inside thebody part 116. Thebooster cylinder chamber 116a extends in the axial direction. Thebooster piston 22A is disposed inside thebooster cylinder chamber 116a so as to be slidable in the axial direction. Thebooster piston 22A is connected to thepiston rod 18A. Amagnet 24 and a packing 23 are attached to an outer circumferential part of thebooster piston 22A. Thebooster piston 22A divides thebooster cylinder chamber 116a into thethird pressure chamber 42 on the head side and afourth pressure chamber 44 on the end side. - The
booster piston 22A is provided with acommunication switching valve 35A switching between communication and non-communication of high-pressure fluid between thethird pressure chamber 42 and thefourth pressure chamber 44, which are adjacent to each other in the axial direction. Thecommunication switching valve 35A includes a through-hole 122 penetrating through thebooster piston 22A in the axial direction and acommunication switching pin 35a inserted into the through-hole 122. - The through-
hole 122 includes an end-side large-diameter part 122a, a small-diameter part 122b, and a head-side large-diameter part 122c. Thecommunication switching pin 35a of thecommunication switching valve 35A is similar to thecommunication switching pin 35a, which has been described with reference toFIG. 3A . Arod part 35d of thecommunication switching pin 35a is inserted into the small-diameter part 122b. A closingpart 35c of thecommunication switching pin 35a is disposed on the end-side large-diameter part 122a side. Thecommunication switching pin 35a protrudes toward the end side by biasing force of a biasingmember 35f. - High-pressure air can flow between the
third pressure chamber 42 and thefourth pressure chamber 44 via the through-hole 122 and aninner channel 35e in thecommunication switching pin 35a. That is, in this embodiment, the through-hole 122 and theinner channel 35e constitute a communication path. When thebooster piston 22A moves toward the end side, thecommunication switching pin 35a is pushed against arod cover 48A. This causes theclosing part 35c and apacking 35b on an outer circumferential part of theclosing part 35c to be inserted into the through-hole 122 to thereby close the through-hole 122. As a result, the communication between thethird pressure chamber 42 and thefourth pressure chamber 44 is blocked. - The
rod cover 48A is disposed adjacent to the end-side end of the end-side body portion 16A and seals the end-side end of thebooster cylinder chamber 116a. Therod cover 48A is provided with anexhaust switching valve 37A switching the discharge state of high-pressure air in thefourth pressure chamber 44. Theexhaust switching valve 37A includes a through-hole 139 penetrating through therod cover 48A in the axial direction and adetection pin 137 inserted into the through-hole 139. - The end-side end of the through-
hole 139 is sealed with acover member 150, and thedetection pin 137 is disposed on the head side of thecover member 150. Thedetection pin 137 is biased toward the head side by a biasing member 140 such as a spring disposed between thecover member 150 and thedetection pin 137. This causes the distal end part of thedetection pin 137 on the head side to protrude inside thefourth pressure chamber 44. -
Annular packings basal end part 138 of thedetection pin 137 at a distance from each other in the axial direction. Thepackings hole 139 and thedetection pin 137. Achannel 143 is disposed between thepackings channel 143 communicates with the through-hole 139, and the outer end thereof communicates with anair channel 144. Theair channel 144 is an annular groove formed in an outer circumferential part of therod cover 48A around the entire circumference and communicates with theadjustment port 32A. A packing 146 is disposed on the head side of theair channel 144, and a packing 148 is disposed on the end side thereof. Thepackings air channel 144 airtight. Theadjustment port 32A can communicate with thefourth pressure chamber 44 via theair channel 144, thechannel 143, and the through-hole 139. That is, in this embodiment, the through-hole 139, thechannel 143, and theair channel 144 constitute an exhaust path. - In a state where the
detection pin 137 is in a head-side position, the through-hole 139 is closed by thepackings fourth pressure chamber 44 is not discharged. When thebooster piston 22A moves to an end-side position, thedetection pin 137 is pushed toward the end side, so that thepackings channel 143. When thepackings channel 143, theadjustment port 32A communicates with thefourth pressure chamber 44. - The
fluid pressure cylinder 10A of this embodiment configured as above is operated by adrive device 120A illustrated inFIGS. 11A and 11B . - As illustrated in
FIG. 11A , thedrive device 120A includes afourth check valve 86, athrottle valve 88, a switchingvalve 102, a high-pressure-air supply source 104, anexhaust port 106, and afifth check valve 108. Thedrive device 120A is configured to supply high-pressure air to thefirst pressure chamber 38 in the workingcylinder chamber 14a during the working process. Moreover, as illustrated inFIG. 11B , thedrive device 120A is configured to supply high-pressure air to thefourth pressure chamber 44 while supplying part of air accumulated in thefirst pressure chamber 38 to thesecond pressure chamber 40 during the return process. - The switching
valve 102 is, for example, a 5-port, 2-position valve including afirst port 102a to afifth port 102e and is switchable between a first position (seeFIG. 11A ) and a second position (seeFIG. 11B ). As illustrated inFIGS. 11A and 11B , thefirst port 102a is connected to the head-side port 28A by pipes. Thesecond port 102b is connected to theadjustment port 32A and the downstream side of thefifth check valve 108 by pipes. Thethird port 102c is connected to theexhaust port 106 by pipes. Thefourth port 102d is connected to the high-pressure-air supply source 104 by pipes. Thefifth port 102e is connected to theexhaust port 106 via thethrottle valve 88 and to the end-side port 30A and the upstream side of thefifth check valve 108 via thefourth check valve 86 by pipes. - As illustrated in
FIG. 11A , when the switchingvalve 102 is in the first position, thefirst port 102a is connected to thefourth port 102d, and thesecond port 102b is connected to thethird port 102c. - Moreover, as illustrated in
FIG. 11B , when the switchingvalve 102 is in the second position, thefirst port 102a is connected to thefifth port 102e, and thesecond port 102b is connected to thefourth port 102d. The switchingvalve 102 is switched between the first position and the second position by pilot pressure from the high-pressure-air supply source 104 or by a solenoid valve. - When the switching
valve 102 is in the second position, thefourth check valve 86 allows air to flow from the head-side port 28A toward the end-side port 30A and blocks air flowing from the end-side port 30A toward the head-side port 28A. Moreover, when the switchingvalve 102 is in the second position, thefifth check valve 108 blocks high-pressure air flowing from thesecond port 102b toward the end-side port 30A. - The
fluid pressure cylinder 10A according to this embodiment and thedrive device 120A are configured as above. Next, the effects and operations thereof will be described. - During the working process of the
fluid pressure cylinder 10A, the switchingvalve 102 of thedrive device 120A is set in the first position as illustrated inFIG. 11A . High-pressure air is supplied from the high-pressure-air supply source 104 to the head-side port 28A via thefirst port 102a of the switchingvalve 102. High-pressure air does not flow toward thefourth check valve 86 since thefourth check valve 86 is connected to thefifth port 102e. Thesecond pressure chamber 40 is connected to theexhaust port 106 via the end-side port 30A and thefifth check valve 108. Theadjustment port 32A is also connected to theexhaust port 106. - As illustrated in
FIG. 10 , during the working process, high-pressure air from the high-pressure-air supply source 104 flows into thefirst pressure chamber 38 through the head-side port 28A. This produces thrust force toward the end side on a workingpiston 20. As a result, thepiston rod 18A moves toward the end side. Note that no thrust force acts on thebooster piston 22A since the high-pressure air enclosed in thethird pressure chamber 42 and thefourth pressure chamber 44 flows therebetween through thecommunication switching valve 35A. - As the working
piston 20 moves, high-pressure air of an amount equal to the volume of thefirst pressure chamber 38 is supplied from the high-pressure-air supply source 104 (seeFIG. 11A ) to thefluid pressure cylinder 10A. During the working process, the pressure of the high-pressure air stored in thethird pressure chamber 42 and the pressure in thefourth pressure chamber 44 are kept constant. Moreover, air in thesecond pressure chamber 40 is discharged from thesecond pressure chamber 40 as the workingpiston 20 moves. In this case, the air in thesecond pressure chamber 40 is discharged from theexhaust port 106 through the end-side port 30A and thefifth check valve 108 as illustrated inFIG. 11A . - As illustrated in
FIG. 12 , as thebooster piston 22A moves, thecommunication switching pin 35a of thecommunication switching valve 35A is pushed toward the head side, while thedetection pin 37a of theexhaust switching valve 37A is pushed toward the end side. - As a result, the closing
part 35c of thecommunication switching pin 35a is inserted into the through-hole 122 and closes the through-hole 122. This blocks the communication of high-pressure air between thethird pressure chamber 42 and thefourth pressure chamber 44. - Moreover, as the
detection pin 37a of theexhaust switching valve 37A is displaced toward the end side, thepackings detection pin 37a and the through-hole 139 are separated from thechannel 143, whereby theadjustment port 32A communicates with thefourth pressure chamber 44. As a result, the high-pressure air stored in thefourth pressure chamber 44 is discharged from theexhaust port 106. That is, the internal pressure in thefourth pressure chamber 44 drops while the high-pressure air is kept in thethird pressure chamber 42. As a result, thrust force corresponding to a difference between the internal pressure in thefourth pressure chamber 44 and the internal pressure in thethird pressure chamber 42 acts on thebooster piston 22A. Since this thrust force is added to the thrust force acting on the workingpiston 20, the thrust force in thefluid pressure cylinder 10A increases near the stroke end. In this manner, in thefluid pressure cylinder 10A, the thrust force is increased by the discharge of the high-pressure air in thefourth pressure chamber 44 while thecommunication switching valve 35A and theexhaust switching valve 37A are being actuated. - During the return process of the
fluid pressure cylinder 10A, the switchingvalve 102 of thedrive device 120A is set in the second position as illustrated inFIG. 11B . High-pressure air is supplied from the high-pressure-air supply source 104 to theadjustment port 32A via thesecond port 102b of the switchingvalve 102. Thefirst port 102a of the switchingvalve 102 is connected to thefifth port 102e, and thereby the head-side port 28A is connected to the end-side port 30A via thefourth check valve 86. The head-side port 28A is also connected to theexhaust port 106 via thethrottle valve 88. As a result, part of the air stored in thefirst pressure chamber 38 is supplied to thesecond pressure chamber 40 via the route with thefourth check valve 86. The remaining part of the air stored in thefirst pressure chamber 38 is discharged from theexhaust port 106. - During the return process, high-pressure air is supplied from the high-pressure-
air supply source 104 to theadjustment port 32A of thefluid pressure cylinder 10A. The high-pressure air supplied to theadjustment port 32A flows into thefourth pressure chamber 44. As a result, high-pressure air discharged during the boosting process is supplemented. As the amount of high-pressure air supplemented at this moment is small compared with the volume of the high-pressure air required for the stroke movement of the working piston, only a small addition of high-pressure air is required. - On the other hand, part of the high-pressure air discharged from the
first pressure chamber 38 flows into thesecond pressure chamber 40. As the air inside thefirst pressure chamber 38 continues to be discharged, a difference between the pressure in thesecond pressure chamber 40 and the pressure in thefirst pressure chamber 38 increases, and the workingpiston 20 starts moving toward the head side. Subsequently, the workingpiston 20 and thebooster piston 22A return to the start-of-stroke position, and the return process is completed. In this manner, thesecond pressure chamber 40 does not need to be supplied with high-pressure air since air required for the workingpiston 20 to return to the start-of-stroke position is supplied from thefirst pressure chamber 38. - The
fluid pressure cylinder 10A according to this embodiment produces the following advantageous effects. - In the
fluid pressure cylinder 10A of this embodiment, high-pressure fluid is enclosed in thethird pressure chamber 42 and thefourth pressure chamber 44, and a boost switching mechanism 33A includes thecommunication switching valve 35A provided in thebooster piston 22A and theexhaust switching valve 37A provided in therod cover 48A. Thefluid pressure cylinder 10A can increase the thrust force at the stroke end without any complicated locking mechanisms. Moreover, since a mechanical locking mechanism for connecting the piston and the piston rod is not required, nonconformity is less likely to occur due to an axial impact, resulting in excellent reliability. - Moreover, in the
fluid pressure cylinder 10A of this embodiment, the diameter of thebooster piston 22A can be made larger than the diameter of the workingpiston 20. Due to thebooster piston 22A with an increased diameter, it is possible to reduce the diameter of the workingpiston 20 while maintaining the thrust force at the stroke end, and thus it is possible to further reduce the consumption of high-pressure air. - The present invention has been described by taking preferred embodiments as examples. However, the present invention is not limited in particular to the above-described embodiments, and various modifications can be made thereto without departing from the scope of the present invention which is defined by the appended claims.
- That is, in the above-described embodiments, the
drive devices fluid pressure cylinders fluid pressure cylinders drive devices cylinder body 12.
Claims (15)
- A fluid pressure cylinder comprising:a cylinder body (12) including a slide hole (12a) extending in an axial direction;a partition wall (26) separating the slide hole into a working cylinder chamber (14a) on a head side and a booster cylinder chamber (16a) on an end side;a working piston (20) disposed in the working cylinder chamber and partitioning the working cylinder chamber into a first pressure chamber (38) on the head side and a second pressure chamber (40) on the end side;a booster piston (22) disposed in the booster cylinder chamber and partitioning the booster cylinder chamber into a third pressure chamber (42) on the head side and a fourth pressure chamber (44) on the end side; anda piston rod (18) connected to the working piston and the booster piston, the piston rod penetrating through the partition wall and protruding out toward the end side;wherein high-pressure fluid is enclosed in two adjacent pressure chambers among the first pressure chamber, the second pressure chamber, the third pressure chamber, and the fourth pressure chamber; andwherein the fluid pressure cylinder further comprises:a boost switching mechanism (33) configured to allow communication of the high-pressure fluid between the two pressure chambers while the working piston is located on the head side of a predetermined position, and configured to, when the working piston moves to the end side of the predetermined position, block the communication of the high-pressure fluid between the two pressure chambers and discharge the high-pressure fluid in one of the two pressure chambers,characterized in that the high-pressure fluid is enclosed in the second pressure chamber and the third pressure chamber; andwherein the boost switching mechanism includes:a communication path (34) communicating with the second pressure chamber and the third pressure chamber;an exhaust path (36) communicating with the second pressure chamber;a communication switching valve (35) configured to open the communication path while the working piston is located on the head side of the predetermined position, and configured to close the communication path when the working piston moves to the end side of the predetermined position; andan exhaust switching valve (37) configured to close the exhaust path while the working piston is located on the head side of the predetermined position, and configured to open the exhaust path to thereby discharge the high-pressure fluid in the second pressure chamber when the working piston moves to the end side of the predetermined position.
- The fluid pressure cylinder according to claim 1, wherein the communication path, the exhaust path, the communication switching valve, and the exhaust switching valve are provided in the partition wall.
- A fluid pressure cylinder comprising:a cylinder body (12) including a slide hole (12a) extending in an axial direction;a partition wall (26) separating the slide hole into a working cylinder chamber (14a) on a head side and a booster cylinder chamber (16a) on an end side;a working piston (20) disposed in the working cylinder chamber and partitioning the working cylinder chamber into a first pressure chamber (38) on the head side and a second pressure chamber (40) on the end side;a booster piston (22) disposed in the booster cylinder chamber and partitioning the booster cylinder chamber into a third pressure chamber (42) on the head side and a fourth pressure chamber (44) on the end side; anda piston rod (18) connected to the working piston and the booster piston, the piston rod penetrating through the partition wall and protruding out toward the end side;wherein high-pressure fluid is enclosed in two adjacent pressure chambers among the first pressure chamber, the second pressure chamber, the third pressure chamber, and the fourth pressure chamber; and wherein the fluid pressure cylinder further comprises:a boost switching mechanism (33) configured to allow communication of the high-pressure fluid between the two pressure chambers while the working piston is located on the head side of a predetermined position, and configured to, when the working piston moves to the end side of the predetermined position, block the communication of the high-pressure fluid between the two pressure chambers and discharge the high-pressure fluid in one of the two pressure chambers,characterized in that the high-pressure fluid is enclosed in the third pressure chamber and the fourth pressure chamber; andwherein the boost switching mechanism includes:a communication path (35e) communicating with the third pressure chamber and the fourth pressure chamber;an exhaust path communicating with the fourth pressure chamber;a communication switching valve configured to open the communication path while the working piston is located on the head side of the predetermined position, and configured to close the communication path when the working piston moves to the end side of the predetermined position; andan exhaust switching valve configured to close the exhaust path while the working piston is located on the head side of the predetermined position, and configured to open the exhaust path to thereby discharge the high-pressure fluid in the fourth pressure chamber when the working piston moves to the end side of the predetermined position.
- The fluid pressure cylinder according to claim 3, wherein the booster piston is provided with the communication path and the communication switching valve.
- The fluid pressure cylinder according to claim 4, further comprising:
a rod cover (48) configured to seal an end-side end of the fourth pressure chamber and provided with the exhaust path and the exhaust switching valve. - The fluid pressure cylinder according to claim 1 or 3, wherein the cylinder body includes an adjustment port (32) communicating with the exhaust path, and the high-pressure fluid is discharged through the exhaust path via the adjustment port.
- The fluid pressure cylinder according to claim 1 or 3, wherein, in the boost switching mechanism, the exhaust switching valve opens the exhaust path after the communication switching valve closes the communication path.
- The fluid pressure cylinder according to any one of claims 1 to 7, wherein the communication switching valve includes a communication switching pin (35a) including a first end that protrudes into one of the two pressure chambers and a second end that is inserted into the communication path, and the communication switching valve is configured to block the communication path when the communication switching pin is pushed in the axial direction as the working piston is displaced.
- The fluid pressure cylinder according to any one of claims 1 to 7, wherein the exhaust switching valve includes a detection pin (37a) including a basal end part that is inserted into the exhaust path to seal the exhaust path and a distal end part that protrudes toward the head side, and the exhaust switching valve is configured to unseal the exhaust path when the detection pin is pushed by the working piston or the booster piston and displaced toward the end side.
- The fluid pressure cylinder according to claim 1 or 2, wherein the exhaust path is provided with a first check valve (52) configured to allow fluid to flow only in a direction along which the fluid is discharged and configured to block fluid flowing in an opposite direction thereof.
- The fluid pressure cylinder according to claim 1 or 2, further comprising:a supplementary channel (78) communicating with the second pressure chamber;wherein the supplementary channel is provided with a second check valve (54) configured to allow fluid to flow toward the second pressure chamber.
- The fluid pressure cylinder according to claim 6, further comprising:an auxiliary path (76) communicating with the fourth pressure chamber and the adjustment port;wherein the auxiliary path is provided with a third check valve (56) configured to allow fluid to flow only in a direction from the fourth pressure chamber toward the adjustment port and configured to block fluid flowing in an opposite direction thereof.
- The fluid pressure cylinder according to claim 1, further comprising:
a drive device (120) connected to the first pressure chamber, the second pressure chamber, and the fourth pressure chamber, wherein:the drive device includes a switching valve (102), a high-pressure-fluid supply source (104), an exhaust port (106), and a fourth check valve (86);when the switching valve is in a first position, the first pressure chamber communicates with the high-pressure-fluid supply source, and the fourth pressure chamber and the boost switching mechanism communicate with the exhaust port; andwhen the switching valve is in a second position, the first pressure chamber communicates with the fourth pressure chamber via the fourth check valve and with the exhaust port, and the second pressure chamber communicates with the high-pressure-fluid supply source. - The fluid pressure cylinder according to claim 3, further comprising:
a drive device (120A) connected to the first pressure chamber, the second pressure chamber, and the fourth pressure chamber, wherein:the drive device includes a switching valve, a high-pressure-fluid supply source, an exhaust port, and a fourth check valve;when the switching valve is in a first position, the first pressure chamber communicates with the high-pressure-fluid supply source, and the fourth pressure chamber and the second pressure chamber communicate with the exhaust port; andwhen the switching valve is in a second position, the first pressure chamber communicates with the second pressure chamber via the fourth check valve and with the exhaust port, and the fourth pressure chamber communicates with the high-pressure-fluid supply source. - The fluid pressure cylinder according to claim 13 or 14, wherein a throttle valve (88) is disposed between the first pressure chamber and the exhaust port.
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
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JP2018171907 | 2018-09-13 | ||
PCT/JP2019/032236 WO2020054322A1 (en) | 2018-09-13 | 2019-08-19 | Hydraulic cylinder |
Publications (3)
Publication Number | Publication Date |
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EP3835600A1 EP3835600A1 (en) | 2021-06-16 |
EP3835600A4 EP3835600A4 (en) | 2022-05-04 |
EP3835600B1 true EP3835600B1 (en) | 2023-08-16 |
Family
ID=69777801
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
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EP19859799.9A Active EP3835600B1 (en) | 2018-09-13 | 2019-08-19 | Hydraulic cylinder |
Country Status (9)
Country | Link |
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EP (1) | EP3835600B1 (en) |
JP (1) | JP7137163B2 (en) |
KR (1) | KR102531495B1 (en) |
CN (1) | CN112689714B (en) |
BR (1) | BR112021004709A2 (en) |
MX (1) | MX2021002864A (en) |
RU (1) | RU2769896C9 (en) |
TW (1) | TWI702344B (en) |
WO (1) | WO2020054322A1 (en) |
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JP7395131B2 (en) * | 2020-04-14 | 2023-12-11 | Smc株式会社 | fluid pressure cylinder |
Family Cites Families (14)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS5224192U (en) * | 1975-08-09 | 1977-02-19 | ||
SU1165818A1 (en) * | 1983-04-01 | 1985-07-07 | Горьковский Конструкторско-Технологический Институт | Booster |
FR2575527B1 (en) * | 1984-12-28 | 1988-08-26 | Telemecanique Electrique | PNEUMATIC OR HYDRAULIC CYLINDER |
EP0738826B1 (en) * | 1995-04-18 | 2000-11-29 | Wärtsilä NSD Schweiz AG | Hydraulic device with differential pistons and its application to a varible thrust drive |
DE19925600A1 (en) * | 1999-06-04 | 2000-12-14 | Sbs Sondermaschinen Gmbh | Light construction hydraulic cylinder has tie rod mounted in outer cylinder tube that bears peripheral forces of hydraulic internal pressure, either outside or inside working chamber |
CN101655112B (en) * | 2009-08-21 | 2011-11-16 | 东莞市安德丰电池有限公司 | Series cylinder |
GB0918364D0 (en) * | 2009-10-21 | 2009-12-02 | Proseal Uk Ltd | Actuator assembly |
US9719521B2 (en) * | 2012-06-18 | 2017-08-01 | Flowserve Management Company | Fluid intensifier for a dry gas seal system |
EP2952750B1 (en) * | 2014-06-04 | 2018-09-05 | MOOG GmbH | Hydraulic system |
JP6665983B2 (en) | 2016-07-26 | 2020-03-13 | Smc株式会社 | Fluid pressure cylinder with booster |
JP6558582B2 (en) * | 2016-08-10 | 2019-08-14 | Smc株式会社 | Fluid pressure device |
JP6673550B2 (en) * | 2016-09-21 | 2020-03-25 | Smc株式会社 | Driving method and driving device for fluid pressure cylinder |
JP6598083B2 (en) * | 2016-12-06 | 2019-10-30 | Smc株式会社 | Piston assembly and fluid pressure device |
JP6598079B2 (en) * | 2016-12-06 | 2019-10-30 | Smc株式会社 | Rod assembly and fluid pressure device |
-
2019
- 2019-08-19 MX MX2021002864A patent/MX2021002864A/en unknown
- 2019-08-19 WO PCT/JP2019/032236 patent/WO2020054322A1/en unknown
- 2019-08-19 EP EP19859799.9A patent/EP3835600B1/en active Active
- 2019-08-19 RU RU2021110015A patent/RU2769896C9/en active
- 2019-08-19 BR BR112021004709-3A patent/BR112021004709A2/en not_active IP Right Cessation
- 2019-08-19 CN CN201980059806.9A patent/CN112689714B/en active Active
- 2019-08-19 KR KR1020217010956A patent/KR102531495B1/en active IP Right Grant
- 2019-08-19 JP JP2020546791A patent/JP7137163B2/en active Active
- 2019-09-11 TW TW108132778A patent/TWI702344B/en active
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JPWO2020054322A1 (en) | 2021-08-30 |
RU2769896C9 (en) | 2022-04-26 |
BR112021004709A2 (en) | 2021-06-01 |
CN112689714A (en) | 2021-04-20 |
KR20210049935A (en) | 2021-05-06 |
EP3835600A1 (en) | 2021-06-16 |
TWI702344B (en) | 2020-08-21 |
JP7137163B2 (en) | 2022-09-14 |
MX2021002864A (en) | 2021-05-28 |
KR102531495B1 (en) | 2023-05-11 |
CN112689714B (en) | 2023-05-16 |
WO2020054322A1 (en) | 2020-03-19 |
RU2769896C1 (en) | 2022-04-07 |
EP3835600A4 (en) | 2022-05-04 |
TW202020318A (en) | 2020-06-01 |
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