WO2018105314A1 - Piston assembly and fluid pressure device - Google Patents

Piston assembly and fluid pressure device Download PDF

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Publication number
WO2018105314A1
WO2018105314A1 PCT/JP2017/040679 JP2017040679W WO2018105314A1 WO 2018105314 A1 WO2018105314 A1 WO 2018105314A1 JP 2017040679 W JP2017040679 W JP 2017040679W WO 2018105314 A1 WO2018105314 A1 WO 2018105314A1
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WO
WIPO (PCT)
Prior art keywords
piston
rod
engaging portion
piston assembly
damper
Prior art date
Application number
PCT/JP2017/040679
Other languages
French (fr)
Japanese (ja)
Inventor
小▲高▼司
Original Assignee
Smc株式会社
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Priority claimed from JP2017025576A external-priority patent/JP6598083B2/en
Application filed by Smc株式会社 filed Critical Smc株式会社
Priority to MX2019006441A priority Critical patent/MX2019006441A/en
Priority to CN201780075451.3A priority patent/CN110073114B/en
Priority to BR112019011573A priority patent/BR112019011573A2/en
Priority to KR1020197019427A priority patent/KR102201138B1/en
Priority to RU2019120892A priority patent/RU2737877C1/en
Priority to US16/466,522 priority patent/US11067173B2/en
Priority to EP17878719.8A priority patent/EP3553326A4/en
Publication of WO2018105314A1 publication Critical patent/WO2018105314A1/en

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B15/00—Fluid-actuated devices for displacing a member from one position to another; Gearing associated therewith
    • F15B15/08—Characterised by the construction of the motor unit
    • F15B15/14—Characterised by the construction of the motor unit of the straight-cylinder type
    • F15B15/1423—Component parts; Constructional details
    • F15B15/1447—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
    • F15B15/20—Other details, e.g. assembly with regulating devices
    • F15B15/22—Other details, e.g. assembly with regulating devices for accelerating or decelerating the stroke
    • F15B15/223—Other details, e.g. assembly with regulating devices for accelerating or decelerating the stroke having a piston with a piston extension or piston recess which completely seals the main fluid outlet as the piston approaches its end position
    • 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
    • F15B15/22—Other details, e.g. assembly with regulating devices for accelerating or decelerating the stroke
    • F15B15/226—Other details, e.g. assembly with regulating devices for accelerating or decelerating the stroke having elastic elements, e.g. springs, rubber pads

Definitions

  • the present invention relates to a piston assembly that reciprocates along a sliding hole and a fluid pressure device.
  • a fluid pressure device including a piston
  • a fluid pressure cylinder having a piston that is displaced under the supply of pressure fluid is known as a conveying means (actuator) for a workpiece or the like.
  • actuator a conveying means
  • a fluid pressure cylinder has a cylinder tube, a piston disposed in the cylinder tube so as to be movable in the axial direction, and a piston rod connected to the piston (see, for example, Japanese Patent Application Laid-Open No. 2014-114874).
  • the piston and the piston rod of the conventional fluid pressure device are assembled by, for example, inserting one end of the piston rod into a hole provided in the center of the piston and crimping (plastically deforming) the one end. It is done. For this reason, a dedicated tool or apparatus is required for assembly, and the assembly work is complicated.
  • the present invention has been made in consideration of such problems, and an object thereof is to provide a piston assembly and a fluid pressure device capable of simplifying the assembling work.
  • the present invention provides a piston assembly including a piston main body that is axially displaceable in a sliding hole, and a piston rod that protrudes axially from the piston main body.
  • the piston main body has a piston-side engaging portion
  • the piston rod has a rod-side engaging portion engaged with the piston-side engaging portion
  • the piston-side engaging portion and the rod-side engaging portion The one engaging portion is engaged with the other engaging portion so as to restrict the axial relative displacement between the piston body and the piston rod by being inserted from the side.
  • One of the piston-side engaging portion and the rod-side engaging portion has a U-shaped, C-shaped or semicircular arc-shaped engaging groove, and the piston-side engaging portion and the rod-side engaging portion
  • the other engaging part of the engaging part may have an annular engaging protrusion inserted into the engaging groove.
  • the engagement groove may be provided in the piston-side engagement portion, and the engagement protrusion may be provided in the rod-side engagement portion.
  • the piston-side engaging portion and the rod-side engaging portion may be engaged with each other so as to be relatively rotatable about the axis of the piston body.
  • damper mechanism that alleviates an impact when reaching at least one stroke end
  • damper mechanism may be supported by the piston body so as not to transmit an impact load to the piston body when reaching the stroke end.
  • the damper mechanism includes an outer peripheral damper disposed on an outer peripheral portion of the piston rod, and a stopper mounting groove extending in a circumferential direction is provided on the outer peripheral portion of the piston rod.
  • a stopper member divided into a plurality in the circumferential direction is mounted, and the outer peripheral damper covers the stopper member, whereby the outer peripheral damper is supported by the stopper member and the stopper member May be prevented from detaching from the stopper mounting groove.
  • the damper mechanism includes an end-side damper disposed on an end surface of the piston rod, and the end-side damper is held between the piston body and the piston rod, and the center of the piston body You may protrude from the through-hole provided in the part.
  • the end side damper may seal between the piston main body and the piston rod.
  • the end side damper may elastically press the end face of the piston rod.
  • This configuration can prevent rattling between the piston body and the piston rod.
  • the piston main body may be made of resin.
  • the piston body may be provided with a lightening portion that surrounds the piston-side engaging portion and has a depth in the axial direction of the piston body.
  • the piston-side engagement portion bulges in the axial direction from the end surface of the piston body and is configured in a U-shape when viewed from the axial direction.
  • a U-shaped engagement is formed on the inner peripheral surface of the piston-side engagement portion.
  • a mating groove may be provided, and the rod-side engagement portion may have an annular engagement protrusion inserted into the U-shaped engagement groove.
  • a ring-shaped outer peripheral damper disposed on the outer peripheral portion of the piston rod for reducing the impact when reaching the stroke end, and a ring-shaped spacer interposed between the piston main body and the outer peripheral damper.
  • the piston main body, the spacer, and the outer peripheral damper are stacked in the axial direction.
  • the present invention is a fluid pressure device including a body having a sliding hole inside, and a piston assembly arranged to be reciprocally movable along the sliding hole, wherein the piston assembly includes: A piston main body that is axially displaceable in the sliding hole, and a piston rod that protrudes axially from the piston main body, the piston main body has a piston-side engagement portion, and the piston rod is It has a rod side engaging part engaged with the piston side engaging part, and one engaging part of the piston side engaging part and the rod side engaging part is inserted into the other engaging part from the side.
  • the piston main body and the piston rod are engaged so as to restrict relative displacement in the axial direction.
  • the fluid pressure device may be configured as a fluid pressure cylinder, a valve device, a length measuring cylinder, a slide table, or a chuck device.
  • the piston side engagement portion and the rod side engagement portion are perpendicular to the axis of the piston body.
  • the piston body and the piston rod can be easily connected by being displaced in the direction and engaged. Further, this assembly can be easily performed manually without using a dedicated tool, equipment or device. Therefore, according to the piston assembly of the present invention, the assembly work can be simplified.
  • FIG. 1 is a cross-sectional view of a fluid pressure cylinder including a piston assembly according to a first embodiment.
  • FIG. 2 is a perspective view of the piston assembly from the piston body side.
  • FIG. 3 is a perspective view of the piston assembly from the piston rod side.
  • 4A is a first explanatory view of a piston assembly method
  • FIG. 4B is a second explanatory view of the piston assembly method
  • FIG. 4C is a third description of the piston assembly method.
  • FIG. FIG. 5 is a cross-sectional view of the piston assembly according to the second embodiment.
  • FIG. 6 is a perspective view of the piston assembly according to the second embodiment.
  • FIG. 7 is a cross-sectional view of the piston assembly according to the third embodiment.
  • FIG. 8A is a cross-sectional view of the piston assembly according to the fourth embodiment
  • FIG. 8B is a cross-sectional view of the piston assembly according to the fifth embodiment
  • FIG. 9A is a cross-sectional view of the piston assembly according to the sixth embodiment
  • FIG. 9B is a cross-sectional view of the piston assembly according to the seventh embodiment
  • FIG. 10A is a cross-sectional view of the piston assembly according to the eighth embodiment
  • FIG. 10B is a cross-sectional view of the piston assembly according to the ninth embodiment
  • FIG. 11 is a cross-sectional view of the piston assembly according to the tenth embodiment
  • FIG. 12 is a cross-sectional view of the piston assembly according to the eleventh embodiment.
  • FIG. 13 is a cross-sectional view of a fluid pressure cylinder including a piston assembly according to a twelfth embodiment.
  • FIG. 14A is a cross-sectional view of a fluid pressure cylinder configured as a single-acting cylinder
  • FIG. 14B is a cross-sectional view of another fluid pressure cylinder configured as a single-acting cylinder.
  • FIG. 15 is a sectional view of a piston assembly according to a thirteenth embodiment. 16 is a perspective view from the piston rod side of the piston assembly shown in FIG.
  • a fluid pressure cylinder 10 ⁇ / b> A shown in FIG. 1 includes a hollow cylindrical cylinder tube 12 (body), a head cover 14 disposed at one end of the cylinder tube 12, and the other end of the cylinder tube 12.
  • a rod cover 16 disposed and a piston assembly 17A disposed so as to be reciprocally movable along the axial direction of the cylinder tube 12 are provided.
  • the piston assembly 17 ⁇ / b> A includes a piston unit 18 that is arranged in the cylinder tube 12 so as to be movable in the axial direction (arrow X direction), and a piston rod 20 that is connected to the piston unit 18.
  • the fluid pressure cylinder 10A is used as an actuator for conveying a workpiece, for example.
  • the cylinder tube 12 is made of, for example, a metal material such as an aluminum alloy, and includes a cylinder that extends along the axial direction. In the present embodiment, the cylinder tube 12 is formed in a hollow cylindrical shape.
  • the cylinder tube 12 includes a first port 12a provided on one end side in the axial direction (arrow X2 direction side), a second port 12b provided on the other end side in the axial direction (arrow X1 direction side), and a first A sliding hole 13 (cylinder chamber) communicating with the port 12a and the second port 12b is provided.
  • the head cover 14 is, for example, a plate-like body made of the same metal material as the cylinder tube 12, and is provided so as to close one end portion (end portion on the arrow X2 direction side) of the cylinder tube 12.
  • One end of the cylinder tube 12 is hermetically closed by the head cover 14.
  • the rod cover 16 is, for example, a circular ring-shaped member made of the same metal material as the cylinder tube 12, and is provided so as to close the other end (the end on the arrow X1 direction side) of the cylinder tube 12. ing.
  • An outer annular groove 24 is formed on the outer periphery of the rod cover 16.
  • An outer seal member 26 made of an elastic material that seals between the outer peripheral surface of the rod cover 16 and the inner peripheral surface of the sliding hole 13 is attached to the outer annular groove 24.
  • An inner annular groove 28 is formed on the inner periphery of the rod cover 16.
  • An inner seal member 30 made of an elastic material that seals between the inner peripheral surface of the rod cover 16 and the outer peripheral surface of the piston rod 20 is attached to the inner annular groove 28.
  • the rod cover 16 is locked by a stopper 32 fixed to the inner peripheral portion on the other end side of the cylinder tube 12.
  • the piston unit 18 is accommodated in the cylinder tube 12 (sliding hole 13) so as to be slidable in the axial direction, and the first pressure chamber 13a on the first port 12a side and the second port 12b side in the sliding hole 13 are accommodated. It is partitioned off from the second pressure chamber 13b.
  • the piston unit 18 is connected to one end 20 a (hereinafter referred to as “base end 20 a”) of the piston rod 20.
  • the piston unit 18 includes a piston main body 38 connected to the piston rod 20, and a packing 34 and a magnet 48 attached to the piston main body 38.
  • the piston main body 38 is an annular member that protrudes radially outward from the base end portion 20a of the piston rod 20.
  • the outer diameter of the piston body 38 is larger than the outer diameter of the piston rod 20.
  • a through hole 38 a penetrating in the axial direction is provided at the center of the piston main body 38.
  • An annular packing mounting groove 36 and an annular magnet mounting groove 49 are provided in the outer peripheral portion of the piston main body 38 (hereinafter referred to as “piston outer peripheral portion 38 b”) with an interval in the axial direction.
  • the piston main body 38 is provided with a piston side engaging portion 40 that engages with a rod side engaging portion 42 described later of the piston rod 20.
  • the piston side engaging part 40 has a shape opened to the side.
  • the piston-side engaging portion 40 is formed in a semicircular arc shape that protrudes in the axial direction from a disk-like wall portion 38 c surrounding the through hole 38 a and partially surrounds the through hole 38 a.
  • an engagement groove 44 is provided in the inner peripheral portion of the piston side engagement portion 40.
  • the engagement groove 44 extends in a semicircular arc shape as in the piston-side engagement portion 40.
  • An inward protrusion 45 that protrudes inward is provided adjacent to the engagement groove 44.
  • the piston side engaging portion 40 (engaging groove 44) is not limited to a semicircular arc shape, and may be formed in a C shape or a U shape.
  • the piston body 38 is provided with a lightening portion 46 that surrounds the piston-side engagement portion 40 and has a depth in the axial direction of the piston body 38. 1 and 3, the lightening portion 46 is formed in an annular shape that opens to the rod cover 16 side, and is provided between the piston-side engaging portion 40 and the magnet mounting groove 49. Note that the lightening portion 46 may be configured by a plurality of holes provided at intervals in the circumferential direction. The meat removal part 46 does not need to be provided.
  • the peripheral wall 49a that forms the bottom of the magnet mounting groove 49 is provided with a hole 50 extending in the circumferential direction.
  • the hole 50 is provided at a position facing the side opening of the piston side engaging portion 40 and penetrates the peripheral wall 49a in the thickness direction.
  • the peripheral wall 49 a is provided with a notch 52 that communicates with the hole 50.
  • the notch 52 has an arc shape obtained by partially notching the inner periphery of the peripheral wall 49a.
  • a surface 38d on the head cover 14 side of the piston main body 38 is provided with a lightening portion 53 that is recessed toward the piston rod 20 side.
  • the lightening portion 53 is formed in an annular shape and is provided between the packing mounting groove 36 and the through hole 38a.
  • the lightening part 53 may be comprised by the some hole provided at intervals in the circumferential direction. The meat extraction part 53 does not need to be provided.
  • the piston body 38 is made of hard resin.
  • the resin-made piston main body 38 can be manufactured by injection molding.
  • the piston body 38 is not limited to resin, and may be made of a metal material such as carbon steel, stainless steel, or aluminum alloy.
  • the packing 34 is an annular seal member (for example, an O-ring) made of an elastic body mounted on the piston outer peripheral portion 38b (packing mounting groove 36).
  • the constituent material of the packing 34 include elastic materials such as rubber materials and elastomer materials.
  • the packing 34 is in airtight or liquid tight contact with the inner peripheral surface of the sliding hole 13 and the piston outer peripheral portion 38b (packing mounting groove 36) over the entire circumference.
  • the seal 34 seals between the outer peripheral surface of the piston unit 18 and the inner peripheral surface of the sliding hole 13, and the first pressure chamber 13a and the second pressure chamber 13b in the sliding hole 13 are partitioned in an airtight or liquid tight manner. ing.
  • the magnet 48 is a circular ring-shaped member, and is mounted on the piston outer peripheral portion 38b (magnet mounting groove 49).
  • the magnet 48 is configured to be elastically deformable.
  • the magnet 48 is a plastic magnet, and has a slit 54 (cut) in a part in the circumferential direction. For this reason, the magnet 48 can be easily mounted by being elastically deformed when mounted in the magnet mounting groove 49.
  • a magnetic sensor (not shown) is attached to the outer surface of the cylinder tube 12 at positions corresponding to both stroke ends of the piston unit 18. The operating position of the piston unit 18 is detected by sensing the magnetism generated by the magnet 48 with a magnetic sensor.
  • the piston rod 20 is a columnar (columnar) member extending along the axial direction of the sliding hole 13.
  • a piston main body 38 is connected to the proximal end portion 20 a of the piston rod 20.
  • a rod-side engagement portion 42 that is engaged with the piston-side engagement portion 40 is provided at the proximal end portion 20 a of the piston rod 20.
  • the piston-side engaging portion 40 and the rod-side engaging portion 42 have an axial relative displacement between the piston main body 38 and the piston rod 20 by inserting one engaging portion into the other engaging portion from the side. It is engaged to regulate.
  • the rod side engaging portion 42 has a T-shape. Specifically, the rod side engaging portion 42 has an annular engaging protrusion 56 inserted into the engaging groove 44.
  • the engagement protrusion 56 extends in an annular shape in the circumferential direction.
  • An annular groove 58 extending annularly in the circumferential direction is provided on the outer peripheral portion of the piston rod 20 adjacent to the engagement protrusion 56.
  • the structure of the piston side engaging portion 40 and the structure of the rod side engaging portion 42 may be replaced with each other. That is, the piston side engaging portion 40 may have a structure having the engaging protrusion 56, and the rod side engaging portion 42 may have a structure having the engaging groove 44.
  • the piston side engaging portion 40 and the rod side engaging portion 42 are engaged with each other so as to be relatively rotatable about the axis a1 of the piston main body 38. Therefore, the piston main body 38 and the piston rod 20 are relatively rotatable around the axis a1 of the piston main body 38.
  • the piston rod 20 penetrates the rod cover 16.
  • a distal end portion 20 b that is an end portion on the opposite side of the proximal end portion 20 a of the piston rod 20 is exposed to the outside of the sliding hole 13.
  • Examples of the constituent material of the piston rod 20 include metal materials such as carbon steel, stainless steel, and aluminum alloy, and hard resin.
  • the piston assembly 17A includes a damper mechanism 60 that reduces the impact when the stroke end is reached.
  • the damper mechanism 60 includes an outer peripheral side damper 62 disposed on the outer peripheral portion of the piston rod 20 and an end portion side damper 64 disposed on the end surface of the piston rod 20.
  • the outer peripheral side damper 62 and the end side damper 64 are made of an elastic material (urethane rubber or the like) such as a rubber material or an elastomer material, for example.
  • the outer periphery side damper 62 alleviates the impact when reaching the stroke end on the rod cover 16 side.
  • the outer periphery side damper 62 is disposed on the rod cover 16 side of the piston body 38 and in the vicinity of the piston body 38.
  • the outer periphery side damper 62 is formed in an annular shape and is disposed so as to surround the piston rod 20.
  • An annular stopper mounting groove 70 is provided in the vicinity of the piston main body 38 on the outer periphery of the piston rod 20.
  • An annular stopper member 72 is mounted in the stopper mounting groove 70.
  • the stopper member 72 includes a plurality of stopper elements 72a divided in the circumferential direction. Each stopper element 72a is formed in an arc shape.
  • the stopper member 72 has a half structure, and is composed of two half-arc shaped stopper elements 72a.
  • the inner peripheral portion of the stopper member 72 (the inner peripheral portion of the stopper element 72 a) is inserted into the stopper mounting groove 70.
  • the stopper member 72 is made of a hard material, for example, the same material as the piston rod 20 described above.
  • the outer periphery side damper 62 covers the stopper member 72 and is attached to the stopper member 72.
  • the outer peripheral damper 62 includes a damper main body 62 a that covers the rod cover 16 side (arrow X1 direction side) of the stopper member 72, and an outer peripheral covering portion 62 b that covers the outer peripheral portion of the stopper member 72.
  • An outer peripheral covering portion 62 b is attached to the outer peripheral portion of the stopper member 72.
  • the outer periphery side damper 62 is supported by the stopper member 72. Further, since the outer peripheral damper 62 is mounted on the stopper member 72, the stopper member 72 is prevented from being detached from the stopper mounting groove 70.
  • the end side damper 64 reduces the impact when the head end of the head cover 14 is reached.
  • the end-side damper 64 is held between the piston main body 38 and the piston rod 20 and protrudes from a through hole 38 a provided in the center of the piston main body 38. In FIG. 1, the end side damper 64 protrudes to the head cover 14 side (arrow X2 direction side) from the surface 38d of the piston main body 38 on the head cover 14 side.
  • the protruding end surface of the end side damper 64 may be positioned closer to the rod cover 16 than the end surface of the piston main body 38 on the head cover 14 side.
  • the piston cover 17A side is disposed on the head cover 14. Protrusions that protrude from the surface are provided.
  • the end side damper 64 has a cylindrical shape (or a disk shape). Specifically, an end portion of the end portion side damper 64 on the piston rod 20 side is provided with an annular flange portion 64a that protrudes radially outward. In FIG. 1, the flange portion 64 a is held between a stepped portion 38 e (reduced diameter portion) provided on the inner peripheral portion of the piston main body 38 and the end surface 20 c of the piston rod 20.
  • the end side damper 64 is in close contact with the inner peripheral portion of the piston main body 38 and the end surface 20 c of the piston rod 20, so that the space between the piston main body 38 and the piston rod 20 is airtight or liquid tight. It is sealed.
  • the end of the end side damper 64 on the side where the flange 64a is provided bulges in the axial direction in a state before assembly (a state before being held between the piston rod 20 and the piston main body 38). It has the bulging part 64b (refer the virtual line of FIG. 1). Thereby, the end side damper 64 elastically presses the end surface 20c of the piston rod 20 in an assembled state (a state held between the piston rod 20 and the piston main body 38). For this reason, rattling between the piston rod 20 and the piston body 38 is suppressed.
  • either the outer peripheral side damper 62 or the end side damper 64 may be omitted, or both the outer peripheral side damper 62 and the end side damper 64 may be omitted.
  • a piston main body 38, a piston rod 20, and an end side damper 64 are prepared.
  • the end side damper 64 is inserted into the through hole 38a of the piston main body 38 from the side where the piston side engaging portion 40 is provided.
  • the piston main body 38 and the piston rod 20 are relatively displaced in the axial direction, and the base end portion 20a (piston side engaging portion 40) of the piston rod 20 is replaced with the piston side engaging portion 40 as shown in FIG. 4B. It inserts between piston outer peripheral parts 38b (thickening part 46).
  • the notch 52 of the piston main body 38 allows the engagement protrusion 56 of the piston rod 20 to pass, and the hole 50 receives a part of the engagement protrusion 56 in the circumferential direction. That is, a part of the engagement protrusion 56 in the circumferential direction passes through the notch 52 of the piston main body 38 and is inserted into the hole 50.
  • the notch 52 and the hole 50 function as escape portions for avoiding the engagement protrusion 56 of the piston rod 20 from interfering with the piston outer peripheral portion 38b.
  • the axis a1 of the piston main body 38 and the axis a2 of the piston rod 20 are shifted from each other, and the rod side engaging portion 42 is located on the side of the piston side engaging portion 40. Therefore, as shown in FIG. 4C, the piston main body 38 and the piston rod 20 are moved relative to each other in a direction perpendicular to the axis a1 of the piston main body 38 so that the axis a1 of the piston main body 38 and the axis a2 of the piston rod 20 coincide.
  • the engagement protrusion 56 is inserted into the engagement groove 44 by being moved. Thereby, the piston side engaging part 40 and the rod side engaging part 42 will be in an engaged state, and the piston main body 38 and the piston rod 20 will be in the connected state.
  • the packing 34 and the magnet 48 are mounted on the piston main body 38, and the stopper member 72 and the outer circumferential damper 62 are mounted on the piston rod 20.
  • the packing 34 and the magnet 48 may be attached to the piston main body 38 before the end side damper 64 and the piston rod 20 are attached to the piston main body 38.
  • the two stopper elements 72a are individually mounted in the stopper mounting groove 70 of the piston rod 20 so as to form the annular stopper member 72. (Fit).
  • the outer circumferential damper 62 is moved from the distal end portion 20b side of the piston rod 20 toward the proximal end portion 20a side, and the outer circumferential damper 62 is placed on the stopper member 72 (two stopper elements 72a). Accordingly, the stopper member 72 is prevented from being detached from the stopper mounting groove 70, and the outer peripheral side damper 62 is held at a predetermined position on the outer peripheral portion of the piston rod 20.
  • the piston assembly 17A shown in FIG. 1 is obtained.
  • the piston unit 18 including the piston body 38 is supported by the cylinder tube 12, and the piston rod 20 is supported by the rod cover 16.
  • the state where the axis a1 of the piston main body 38 and the axis a2 of the piston rod 20 coincide with each other is maintained. Therefore, the engagement between the piston side engaging portion 40 and the rod side engaging portion 42 is maintained.
  • the fluid pressure cylinder 10A moves the piston unit 18 in the axial direction in the sliding hole 13 by the action of the pressure fluid (for example, compressed air) introduced through the first port 12a or the second port 12b. Thereby, the piston rod 20 connected to the piston unit 18 moves forward and backward.
  • the pressure fluid for example, compressed air
  • the second port 12b is opened to the atmosphere, and pressure fluid is supplied from a pressure fluid supply source (not shown) through the first port 12a.
  • a pressure fluid supply source not shown
  • One pressure chamber 13a is supplied.
  • the piston unit 18 is pushed toward the rod cover 16 by the pressure fluid.
  • the piston unit 18 is displaced (advanced) together with the piston rod 20 toward the rod cover 16 side.
  • the forward movement of the piston unit 18 is stopped when the outer circumferential damper 62 contacts the end face of the rod cover 16.
  • the piston body 38 and the rod cover 16 are prevented from coming into direct contact with each other by the outer peripheral damper 62 made of an elastic material. Thereby, it is possible to effectively prevent or suppress the generation of impact and impact sound associated with the piston main body 38 reaching the forward position (stroke end on the rod cover 16 side).
  • the first port 12a is opened to the atmosphere, and pressure fluid is supplied from a pressure fluid supply source (not shown) through the second port 12b to the second pressure chamber. 13b. Then, the piston unit 18 is pushed toward the head cover 14 by the pressure fluid. As a result, the piston unit 18 is displaced toward the head cover 14 side.
  • the piston main body 38 has the piston side engaging portion 40, and the piston rod 20 is engaged with the piston side engaging portion 40.
  • the piston-side engaging portion 40 and the rod-side engaging portion 42 are inserted in the axial direction between the piston main body 38 and the piston rod 20 by inserting one engaging portion into the other engaging portion from the side. Engages so as to regulate relative displacement.
  • the piston side engaging portion 40 and the rod side engaging portion 42 are displaced in a direction perpendicular to the axis a1 of the piston main body 38.
  • this assembly can be easily performed manually without using a dedicated tool, equipment or device. Therefore, according to the piston assembly 17A of the present invention, the assembly work can be simplified.
  • one of the piston-side engagement portion 40 and the rod-side engagement portion 42 has a U-shaped, C-shaped, or semicircular arc-shaped engagement groove 44, and the piston-side engagement
  • the other engaging portion of the portion 40 and the rod side engaging portion 42 has an annular engaging protrusion 56 inserted into the engaging groove 44.
  • the piston-side engagement portion 40 and the rod-side engagement portion 42 are engaged with each other so as to be relatively rotatable about the axis a1 of the piston body 38.
  • the piston rod 20 can be easily rotated when the fluid pressure cylinder 10A is installed in the facility, which is convenient.
  • the piston rod 20 can be rotated in the same manner for a piston assembly 17B (FIGS. 5 and 6) including a polygonal piston main body 38A described later.
  • the damper mechanism 60 is provided to reduce the impact when the stroke end is reached, and the damper mechanism 60 is supported by the piston body 38 so as not to transmit the impact load to the piston body 38 when the stroke end is reached. Therefore, the piston main body 38 only needs to be designed to have a strength that can withstand the pressure from the working fluid, and can be made of resin. That is, even in the case of the resin piston main body 38, practical durability is easily obtained. By making the piston body 38 of resin, the weight of the piston assembly 17A can be reduced.
  • the damper mechanism 60 has an outer periphery side damper 62 disposed on the outer periphery of the piston rod 20, and a stopper mounting groove 70 extending in the circumferential direction is provided on the outer periphery of the piston rod 20. ing.
  • the stopper mounting groove 70 is mounted with a stopper member 72 divided into a plurality in the circumferential direction.
  • the outer circumferential damper 62 covers the stopper member 72, whereby the outer circumferential damper 62 is supported by the stopper member 72 and the stopper member 72 is prevented from being detached from the stopper mounting groove 70.
  • the damper mechanism 60 has an end-side damper 64 disposed on the end surface 20 c of the piston rod 20, and the end-side damper 64 is held between the piston body 38 and the piston rod 20. At the same time, it protrudes from a through hole 38 a provided at the center of the piston body 38. With the end side damper 64 having such a configuration, it is possible to satisfactorily prevent the impact load from being transmitted to the piston body 38 when the other stroke end is reached.
  • the end side damper 64 seals between the piston main body 38 and the piston rod 20. Therefore, since the end side damper 64 also serves as a seal member between the piston main body 38 and the piston rod 20, the number of parts can be reduced as compared with a configuration in which the damper and the seal member are provided as separate parts. .
  • the end-side damper 64 elastically presses the end surface 20c of the piston rod 20. With this configuration, rattling between the piston body 38 and the piston rod 20 can be prevented.
  • the piston main body 38 is provided with a lightening portion 46 that surrounds the piston-side engaging portion 40 and has a depth in the axial direction of the piston main body 38. For this reason, weight reduction of the piston assembly 17A including the piston main body 38 is achieved. Further, by reducing the weight of the piston assembly 17A, the amount of pressure fluid consumed can be reduced, and energy saving can be achieved.
  • the present invention can be applied not only to the above-described circular piston body 38 but also to a polygonal piston body 38. Therefore, in the fluid pressure cylinder, instead of the piston assembly 17A having the circular piston body 38, a piston assembly 17B having the polygonal piston body 38A shown in FIGS. 5 and 6 may be employed.
  • the piston body 38A of the piston assembly 17B has an octagonal shape.
  • the piston body 38A is provided with a plurality of magnet mounting grooves 74 at intervals in the circumferential direction.
  • the plurality of magnet mounting grooves 74 are provided on one surface of the piston main body 38A and have a depth in the axial direction of the piston main body 38A.
  • a magnet 76 is mounted in one magnet mounting groove 74.
  • the magnet 76 is, for example, a ferrite magnet or a rare earth magnet.
  • An annular packing mounting groove 78 is provided on the outer peripheral portion of the piston main body 38A.
  • the bottom of the packing mounting groove 78 extends in an annular shape in the circumferential direction.
  • a packing 79 made of an elastic member is mounted in the packing mounting groove 78.
  • the outer peripheral part shape of the packing 79 is formed in the same polygon (an octagon in the case of FIG. 6) as the piston main body 38A.
  • the inner peripheral shape of the packing 79 is circular.
  • the other part of the piston assembly 17B is configured in the same manner as the piston assembly 17A.
  • piston assembly 17B the same effects as the piston assembly 17A can be obtained, for example, it can be easily assembled manually without using a dedicated tool, equipment or device.
  • piston rod 20 having a solid structure is employed, but a piston rod 20A having a hollow structure may be employed as in the piston assembly 17C shown in FIG. With this configuration, it is possible to obtain a piston assembly 17C that is further reduced in weight and energy. Note that the opening on one end side of the piston rod 20 ⁇ / b> A is airtightly or liquid tightly closed by the end side damper 64.
  • piston rod 20 protruding only on one side of the piston main body 38 is adopted.
  • Piston rods 82 and 84 protruding on both sides of the main body 38B may be employed.
  • first piston side engaging portion 40A and “second piston side engaging portion 40B”
  • first piston side engaging portion 40A and “second piston side engaging portion 40B”
  • the piston rod 82 includes a first rod 82A that engages with the first piston-side engaging portion 40A and a second rod 82B that engages with the second piston-side engaging portion 40B.
  • the first rod 82A and the second rod 82B are configured similarly to the piston rod 20 described above, and have a solid structure.
  • An intermediate member 83 is interposed between the first rod 82A and the second rod 82B.
  • the intermediate member 83 may be made of an elastic material similar to that of the outer peripheral side damper 62 described above. Thereby, the intermediate member 83 presses the end surface 82A1 of the first rod 82A and the end surface 82B1 of the second rod 82B, and rattling between the piston main body 38B and the first rod 82A is suppressed, and the piston main body 38B and the first The backlash between the two rods 82B is suppressed.
  • the intermediate member 83 is in close contact with the piston main body 38B, the first rod 82A, and the second rod 82B, thereby also serving as an air seal for the first rod 82A side and the second rod 82B side.
  • outer peripheral side dampers 62 are disposed on the outer peripheral portions of the first rod 82A and the second rod 82B, respectively, and stoppers mounted on the first rod 82A and the second rod 82B.
  • the outer periphery side dampers 62 are supported by the members 72, respectively.
  • a piston assembly 17E shown in FIG. 8B is obtained by changing the first rod 82A, the second rod 82B, and the intermediate member 83 in the piston assembly 17D shown in FIG. 8A to a hollow structure. That is, the piston assembly 17E includes a piston main body 38B and hollow piston rods 84 (first rod 84A and second rod 84B) connected to the piston main body 38B, and the first rod 84A and the second rod. A hollow intermediate member 83a is interposed between 84B and 84B.
  • both the outer peripheral side damper 62 and the end side damper 64 are provided in the piston assembly 17A (FIG. 1).
  • the outer peripheral side damper 62 is used as a damper mechanism. May be provided.
  • the piston body 38C of the piston assembly 17F is configured in the same manner as the piston body 38 of the piston assembly 17A, except that a through hole penetrating in the axial direction is not provided.
  • only the end side damper 64 may be provided as the damper mechanism (the outer peripheral side damper 62 may be omitted in the piston assembly 17A).
  • the damper mechanism may not be provided.
  • the magnet 48 may be omitted.
  • the magnet mounting groove 49 may be left in the piston main body 38 as in the piston assembly 17H shown in FIG. 10A.
  • the piston main body 38D which abbreviate
  • piston assembly 17A when the piston main body 38 is made of a low friction material, the piston outer peripheral portion 38b functions as a wear ring.
  • a piston body 38E provided with an annular wear ring mounting groove 86 is employed, and a wear ring 88 made of a low friction material is mounted in the wear ring mounting groove 86. May be.
  • Wear ring 88 is an annular member for preventing the outer peripheral surface of piston body 38E from contacting the inner peripheral surface of sliding hole 13 (FIG. 1).
  • the outer diameter of the wear ring 88 is larger than the outer shape of the piston main body 38E.
  • the low friction material include a synthetic resin material having both low friction and wear resistance such as tetrafluoroethylene (PTFE), a metal material (for example, bearing steel), and the like.
  • a piston main body 38F to which no magnet and wear ring are attached is adopted, and the damper mechanism may be omitted.
  • a fluid pressure cylinder 10B shown in FIG. 13 includes a hollow cylindrical cylinder tube 102 (body), a head cover 104 disposed at one end of the cylinder tube 102, and a rod cover 106 disposed at the other end of the cylinder tube 102.
  • the fluid pressure cylinder 10B further includes a piston assembly 17L disposed so as to be reciprocally movable with respect to the cylinder tube 102, a damper mechanism 60A, and a cushion mechanism 110 that alleviates an impact at one and the other stroke ends of the piston unit 18.
  • the piston assembly 17L includes a piston unit 18 disposed in the cylinder tube 102 so as to be movable in the axial direction (arrow X direction), and a piston rod 108 coupled to the piston unit 18.
  • the cylinder tube 102 is formed of a cylindrical body, and a sliding hole 103 (cylinder chamber) in which the piston unit 18 is accommodated and closed by the head cover 104 and the rod cover 106 is formed.
  • the first stepped portion 112 of the head cover 104 is inserted into the end of the cylinder tube 102 on the arrow X2 direction side.
  • the head cover 104 is formed with a first central cavity 116 and a first port 118 communicating with the first central cavity 116. Pressure fluid is supplied and discharged through the first port 118.
  • the second stepped portion 120 of the rod cover 106 is inserted into the end of the cylinder tube 102 on the arrow X1 direction side.
  • the rod cover 106 is formed with a second central cavity portion 124 and a second port 126 communicating with the second central cavity portion 124. Pressure fluid is supplied and discharged through the second port 126.
  • a ring-shaped bush 130 and packing 132 are disposed on the inner peripheral portion of the rod cover 106.
  • the piston unit 18 is configured similarly to the piston unit 18 of the piston assembly 17A (FIG. 1).
  • the damper mechanism 60A includes an outer peripheral damper 62 (same configuration as the outer peripheral damper 62 shown in FIG. 1) disposed on the outer periphery of the piston rod 108, an end damper 64A disposed on the end surface 108a of the piston rod 108, Have The outer peripheral damper 62 is located at the end of the second cushion member 142 on the piston main body 38 side.
  • the end side damper 64 ⁇ / b> A is obtained by modifying the end side damper 64 (FIG. 1) into a hollow shape, and is held between the end surface 108 a of the piston rod 108 and the inner peripheral portion of the piston main body 38.
  • the cushion mechanism 110 includes a first cushion member 140 and a second cushion member 142 (cushion ring) provided on the movable portion (piston rod 108) side, and an elasticity provided on the fixed portion (head cover 104 and rod cover 106) side. It has the ring-shaped 1st cushion seal 144 and 2nd cushion seal 146 which consist of members.
  • the first cushion member 140 is provided coaxially with the piston rod 108 at the end of the piston rod 108 on the arrow X2 direction side. Specifically, the first cushion member 140 is formed with a smaller diameter than the piston rod 108, and protrudes in the direction of the arrow X2 from the end surface 108a of the piston rod 108 and the end surface of the end-side damper 64A.
  • the first cushion member 140 is formed in a hollow or solid cylindrical shape. The outer diameter of the first cushion member 140 is smaller than the outer diameter of the end side damper 64A.
  • the first cushion member 140 may be a part formed integrally with the piston rod 108 or may be a separate part joined to the piston rod 108. When the first cushion member 140 is a separate component from the piston rod 108, the first cushion member 140 can be joined to the piston rod 108 by joining means such as welding, adhesion, and screwing.
  • the first cushion seal 144 is held on the inner periphery of the ring-shaped first holder 148.
  • the first holder 148 is fixed to the inner peripheral portion of the first stepped portion 112 of the head cover 104.
  • the sliding hole 103 and the first central cavity 116 communicate with each other via the hole 148a.
  • the first cushion seal 144 is in sliding contact with the outer peripheral surface of the first cushion member 140 over the entire circumference.
  • the second cushion member 142 is adjacent to the rod cover 106 side (arrow X1 direction side) of the piston unit 18 and is provided coaxially with the piston rod 108 in the vicinity of the piston unit 18.
  • the second cushion member 142 is a ring-shaped member having a larger diameter than the piston rod 108 and a smaller diameter than the piston unit 18, and is joined to the outer peripheral surface of the piston rod 108 by, for example, welding or adhesion. Yes.
  • the outer diameter of the second cushion member 142 is slightly larger than the outer diameter of the piston rod 108.
  • the second cushion seal 146 is held on the inner periphery of the ring-shaped second holder 150.
  • the second holder 150 is fixed to the inner peripheral portion of the second stepped portion 120 of the rod cover 106.
  • the sliding hole 103 and the second central cavity 124 communicate with each other through the hole 150a.
  • the second cushion seal 146 is in sliding contact with the outer peripheral surface of the second cushion member 142 over the entire circumference.
  • the fluid pressure cylinder 10 ⁇ / b> B moves the piston unit 18 in the axial direction in the sliding hole 103 by the action of the pressure fluid introduced through the first port 118 or the second port 126. Thereby, the piston rod 108 connected to the piston unit 18 moves forward and backward.
  • the second port 126 is opened to the atmosphere, and the first port 118 and the first central cavity 116 116 from a pressure fluid supply source (not shown).
  • air is supplied to the first pressure chamber 103a through the hole 148a.
  • the piston unit 18 is displaced (advanced) together with the piston rod 108 toward the rod cover 106 side.
  • the air in the second pressure chamber 103 b is discharged from the second port 126 through the hole 150 a of the second holder 150 and the second central cavity 124.
  • the outer peripheral damper 62 may be formed in the magnitude
  • the second cushion member 142 When the piston unit 18 approaches the forward position, the second cushion member 142 is inserted into the hole 150a of the second holder 150. Accordingly, the inner peripheral portion of the second cushion seal 146 contacts the outer peripheral surface of the second cushion member 142, and an airtight seal is formed at this contact portion.
  • an air cushion is formed in the second pressure chamber 103b.
  • the air cushion in the second pressure chamber 103b serves as a displacement resistance when the piston unit 18 is displaced toward the rod cover 106, thereby decelerating the displacement of the piston unit 18 near the stroke end on the rod cover 106 side. Therefore, the impact when the piston unit 18 reaches the stroke end is further alleviated.
  • the air is exhausted little by little to the second port 126 through a small hole (not shown).
  • the first port 118 is opened to the atmosphere, and the second port 126 and the second center are connected from a pressure fluid supply source (not shown). Air is supplied to the second pressure chamber 103b through the cavity 124 and the hole 150a. As a result, the piston unit 18 is displaced (retracted) toward the head cover 104 side. In this case, the air in the first pressure chamber 103 a is discharged from the first port 118 through the hole 148 a of the first holder 148 and the first central cavity 116. Then, when the end side damper 64A comes into contact with the first holder 148, the backward movement of the piston unit 18 is stopped.
  • the first cushion member 140 When the piston unit 18 approaches the retracted position, the first cushion member 140 is inserted into the hole 148a of the first holder 148. Accordingly, the inner peripheral portion of the first cushion seal 144 comes into contact with the outer peripheral surface of the first cushion member 140, and an airtight seal is formed at this contact portion.
  • the air cushion in the first pressure chamber 103a serves as a displacement resistance when the piston unit 18 is displaced toward the head cover 104, thereby decelerating the displacement of the piston unit 18 near the stroke end on the head cover 104 side. Therefore, the impact when the piston unit 18 reaches the stroke end is further alleviated.
  • the fluid pressure cylinder 10C shown in FIG. 14A is configured as a so-called single acting cylinder. Specifically, the fluid pressure cylinder 10 ⁇ / b> C is obtained by arranging a spring 154 between the piston unit 18 and the rod cover 16 in the fluid pressure cylinder 10 ⁇ / b> A (FIG. 1). In this case, the second port 12b is open to the atmosphere.
  • the piston unit 18 In the fluid pressure cylinder 10C, when pressure fluid is supplied to the first pressure chamber 13a via the first port 12a, the piston unit 18 is displaced (advanced) toward the rod cover 16 by the pressure fluid, and the stroke end of the advance position is reached. And reach.
  • the piston unit 18 When the supply of pressurized fluid to the first port 12a is stopped and the first port 12a is opened to the atmosphere, the piston unit 18 is displaced (retracted) toward the head cover 14 by the elastic biasing force of the spring 154, and the retracted position. To reach the stroke end.
  • the fluid pressure cylinder 10D shown in FIG. 14B is also configured as a so-called single acting cylinder. Specifically, the fluid pressure cylinder 10 ⁇ / b> D is obtained by arranging a spring 154 between the piston unit 18 and the head cover 14 in the fluid pressure cylinder 10 ⁇ / b> A (FIG. 1). In this case, the first port 12a is open to the atmosphere.
  • the piston unit 18 In the fluid pressure cylinder 10D, when the pressure fluid is supplied to the second pressure chamber 13b via the second port 12b, the piston unit 18 is displaced (retracted) toward the head cover 14 by the pressure fluid, and the stroke end of the retracted position is reached. To reach. When the supply of the pressure fluid to the second port 12b is stopped and the second port 12b is opened to the atmosphere, the piston unit 18 is displaced (advanced) to the rod cover 16 side by the elastic biasing force of the spring 154, and advances. The stroke end of the position is reached.
  • a piston assembly 17M shown in FIGS. 15 and 16 may be employed.
  • the piston assembly 17M includes a piston unit 18a and a piston rod 160 connected to the piston unit 18a.
  • the piston unit 18 a includes a piston main body 162 connected to the piston rod 160, and a packing 34 and a magnet 48 attached to the outer periphery of the piston main body 162.
  • the constituent material of the piston main body 162 can be selected from the materials exemplified as the constituent material of the piston main body 38 (FIG. 1 and the like) described above.
  • An end side damper 64 is disposed between the piston main body 162 and the piston rod 160. The end side damper 64 is attached to a through hole 162 a provided in the piston main body 162.
  • the piston main body 162 is provided with a piston-side engaging portion 166 by integral molding.
  • the piston side engaging portion 166 has a shape opened to the side.
  • the piston-side engaging portion 166 bulges in the axial direction (arrow X direction) from the end surface 162 b of the piston main body 162 and is configured in a U shape when viewed from the axial direction.
  • a U-shaped engagement groove 166 a is provided on the inner peripheral surface of the piston-side engagement portion 166.
  • the piston-side engaging portion 166 includes a curved portion 167 extending in an arc shape along the outer peripheral shape of the through hole 162a, and two arm portions 168 extending linearly and parallel to each other from both ends of the curved portion 167. And have. When viewed from the axial direction of the piston main body 162, the distal ends of the two arm portions 168 are located radially outside of the through hole 162a.
  • the piston main body 162 is provided with the piston-side engaging portion 166 configured in a U-shape.
  • the piston side engaging part 166 functions as a reinforcing rib, and the piston main body 162 is reinforced.
  • operation of the fluid pressure cylinder in which the piston assembly 17M was integrated can be improved.
  • a rod side engaging portion 42 engaged with the U-shaped engaging groove 166a of the piston side engaging portion 166 is provided.
  • the rod side engaging portion 42 is configured by an annular engaging protrusion 56.
  • An annular groove 58 is formed adjacent to the engagement protrusion 56.
  • a ring-shaped outer peripheral damper 170 made of an elastic material that relieves an impact when reaching the stroke end in the direction of the arrow X1 is disposed.
  • a ring-shaped spacer 172 is interposed between the piston main body 162 and the outer peripheral side damper 170. The spacer 172 is in contact with the piston side engaging portion 166.
  • the piston main body 162, the spacer 172, and the outer peripheral side damper 170 are laminated in the axial direction.
  • the spacer 172 is made of a material harder than the outer peripheral damper 170.
  • the constituent material of the spacer 172 may be selected from the materials listed as the constituent material of the piston rod 20 (FIG. 1 and the like) described above.
  • the load when reaching the stroke end in the direction of the arrow X1 is transmitted to the piston main body 162 via the outer peripheral damper 170. Accordingly, the piston body 162 receives a load when the stroke end is reached.
  • the piston main body 162 is made of a metal material, the strength of the piston main body 162 can be sufficiently secured because the strength is higher than that of the resin material.
  • a ring-shaped spacer 172 that is harder than the outer peripheral damper 170 is interposed between the piston main body 162 and the outer peripheral damper 170, so that the outer peripheral damper 170 has a U-shaped piston side.
  • the entire periphery is supported not by the engaging portion 166 but by the ring-shaped spacer 172. Therefore, it is possible to prevent the outer peripheral damper 170 made of an elastic material from being damaged by a load when reaching the stroke end.
  • the present invention is not limited to the above-described embodiment, and various modifications can be made without departing from the gist of the present invention.
  • the present invention can also be applied to a hydraulic cylinder whose piston unit and cylinder tube have non-circular cross-sectional shapes (such as a square shape or an elliptical shape such as an elliptical shape) (the piston assembly 17B in FIG. One example).
  • the present invention can also be applied to a multi-rod type (dual rod type or the like) fluid pressure cylinder having a plurality of pistons and piston rods.
  • the present invention is not limited to a fluid pressure cylinder used as an actuator or the like, but can be applied to other forms of fluid pressure devices having a piston.
  • Other forms of fluid pressure devices having a piston to which the present invention can be applied include, for example, a valve device that switches a flow path by moving a valve body by a piston, and a piston that is connected to the piston rod as an input shaft.
  • a measuring cylinder that measures the length by displacing it, a slide table that displaces the table that is connected to the piston via the piston rod by displacing the piston, and a grip that opens and closes by displacing the piston and converting this piston displacement
  • a chuck device for gripping a workpiece by the portion.

Abstract

According to the present invention, a fluid pressure cylinder (10A) includes a piston assembly (17A). A piston main body (38) of the piston assembly (17A) includes a piston-side engagement part (40). A piston rod (20) includes a rod-side engagement part (42) that engages the piston-side engagement part (40). One of the piston-side engagement part (40) and the rod-side engagement part (42) is inserted into the other from the side, and the engagement parts thereby engage so as to restrict mutual displacement between the piston main body (38) and the piston rod (20) in the axial direction.

Description

ピストン組立体及び流体圧装置Piston assembly and fluid pressure device
　本発明は、摺動孔に沿って往復動作するピストン組立体及び流体圧装置に関する。 The present invention relates to a piston assembly that reciprocates along a sliding hole and a fluid pressure device.
　従来、ピストンを備えた流体圧装置としては種々の装置が知られている。例えばワーク等の搬送手段（アクチュエータ）として、圧力流体の供給作用下に変位するピストンを有する流体圧シリンダは公知である。一般に流体圧シリンダは、シリンダチューブと、シリンダチューブ内に軸方向に移動可能に配置されたピストンと、ピストンに連結されたピストンロッドとを有する（例えば、特開２０１４－１１４８７４号公報参照）。このような流体圧シリンダにおいて、空気等の圧力流体がシリンダチューブ内に供給されると、ピストンが圧力流体によって押されることで軸方向に変位し、ピストンに連結されたピストンロッドも軸方向に変位する。 Conventionally, various devices are known as a fluid pressure device including a piston. For example, a fluid pressure cylinder having a piston that is displaced under the supply of pressure fluid is known as a conveying means (actuator) for a workpiece or the like. Generally, a fluid pressure cylinder has a cylinder tube, a piston disposed in the cylinder tube so as to be movable in the axial direction, and a piston rod connected to the piston (see, for example, Japanese Patent Application Laid-Open No. 2014-114874). In such a fluid pressure cylinder, when a pressure fluid such as air is supplied into the cylinder tube, the piston is displaced in the axial direction by being pushed by the pressure fluid, and the piston rod connected to the piston is also displaced in the axial direction. To do.
　ところで、従来の流体圧装置のピストンとピストンロッドは、例えば、ピストンロッドの一端部をピストン中心部に設けられた孔部に挿入し、当該一端部を加締める（塑性変形させる）ことにより、組み立てられる。このため、組立てに際して専用工具又は装置を必要とするとともに、組立作業が煩雑である。 By the way, the piston and the piston rod of the conventional fluid pressure device are assembled by, for example, inserting one end of the piston rod into a hole provided in the center of the piston and crimping (plastically deforming) the one end. It is done. For this reason, a dedicated tool or apparatus is required for assembly, and the assembly work is complicated.
　本発明はこのような課題を考慮してなされたものであり、組立作業を簡素化することが可能なピストン組立体及び流体圧装置を提供することを目的とする。 The present invention has been made in consideration of such problems, and an object thereof is to provide a piston assembly and a fluid pressure device capable of simplifying the assembling work.
　上記の目的を達成するため、本発明は、摺動孔内を軸方向に変位可能なピストン本体と、前記ピストン本体から軸方向に突出したピストンロッドとを備えたピストン組立体であって、前記ピストン本体は、ピストン側係合部を有し、前記ピストンロッドは、前記ピストン側係合部に係合したロッド側係合部を有し、前記ピストン側係合部と前記ロッド側係合部は、一方の係合部が他方の係合部に側方から挿入されることにより、前記ピストン本体と前記ピストンロッドとの軸方向の相対変位を規制するように係合していることを特徴とする。 In order to achieve the above object, the present invention provides a piston assembly including a piston main body that is axially displaceable in a sliding hole, and a piston rod that protrudes axially from the piston main body. The piston main body has a piston-side engaging portion, and the piston rod has a rod-side engaging portion engaged with the piston-side engaging portion, and the piston-side engaging portion and the rod-side engaging portion The one engaging portion is engaged with the other engaging portion so as to restrict the axial relative displacement between the piston body and the piston rod by being inserted from the side. And
　前記ピストン側係合部及び前記ロッド側係合部の一方の係合部は、Ｕ字状、Ｃ字状又は半円弧状の係合溝を有し、前記ピストン側係合部及び前記ロッド側係合部の他方の係合部は、前記係合溝に挿入された環状の係合突起を有してもよい。 One of the piston-side engaging portion and the rod-side engaging portion has a U-shaped, C-shaped or semicircular arc-shaped engaging groove, and the piston-side engaging portion and the rod-side engaging portion The other engaging part of the engaging part may have an annular engaging protrusion inserted into the engaging groove.
　前記係合溝は、前記ピストン側係合部に設けられており、前記係合突起は、前記ロッド側係合部に設けられていてもよい。 The engagement groove may be provided in the piston-side engagement portion, and the engagement protrusion may be provided in the rod-side engagement portion.
　前記ピストン側係合部及び前記ロッド側係合部は、前記ピストン本体の軸を中心に相対回転可能に係合していてもよい。 The piston-side engaging portion and the rod-side engaging portion may be engaged with each other so as to be relatively rotatable about the axis of the piston body.
　少なくとも一方のストロークエンド到達時の衝撃を緩和するダンパ機構を備え、前記ダンパ機構は、ストロークエンド到達時に前記ピストン本体に衝撃荷重を伝達しないように前記ピストン本体に支持されていてもよい。 It may be provided with a damper mechanism that alleviates an impact when reaching at least one stroke end, and the damper mechanism may be supported by the piston body so as not to transmit an impact load to the piston body when reaching the stroke end.
　前記ダンパ機構は、前記ピストンロッドの外周部に配置された外周側ダンパを有し、前記ピストンロッドの前記外周部には、周方向に延在するストッパ装着溝が設けられ、前記ストッパ装着溝には、周方向に複数に分割されたストッパ部材が装着されており、前記外周側ダンパは前記ストッパ部材を覆っており、これにより、前記外周側ダンパが前記ストッパ部材により支持されるとともに前記ストッパ部材が前記ストッパ装着溝から離脱することが阻止されていてもよい。 The damper mechanism includes an outer peripheral damper disposed on an outer peripheral portion of the piston rod, and a stopper mounting groove extending in a circumferential direction is provided on the outer peripheral portion of the piston rod. A stopper member divided into a plurality in the circumferential direction is mounted, and the outer peripheral damper covers the stopper member, whereby the outer peripheral damper is supported by the stopper member and the stopper member May be prevented from detaching from the stopper mounting groove.
　前記ダンパ機構は、前記ピストンロッドの端面に配置された端部側ダンパを有し、前記端部側ダンパは、前記ピストン本体と前記ピストンロッドとの間に保持されるとともに、前記ピストン本体の中心部に設けられた貫通孔から突出していてもよい。 The damper mechanism includes an end-side damper disposed on an end surface of the piston rod, and the end-side damper is held between the piston body and the piston rod, and the center of the piston body You may protrude from the through-hole provided in the part.
　前記端部側ダンパは、前記ピストン本体と前記ピストンロッドとの間をシールしていてもよい。 The end side damper may seal between the piston main body and the piston rod.
　前記端部側ダンパは、前記ピストンロッドの前記端面を弾性的に押圧していてもよい。 The end side damper may elastically press the end face of the piston rod.
　この構成により、ピストン本体とピストンロッドとの間のガタツキを防止することができる。 This configuration can prevent rattling between the piston body and the piston rod.
　前記ピストン本体は、樹脂製であってもよい。 The piston main body may be made of resin.
　前記ピストン本体には、前記ピストン側係合部を囲むとともに前記ピストン本体の軸方向に深さを有する肉抜き部が設けられていてもよい。 The piston body may be provided with a lightening portion that surrounds the piston-side engaging portion and has a depth in the axial direction of the piston body.
　前記ピストン側係合部は、前記ピストン本体の端面から軸方向に膨出するとともに軸方向から見てＵ字状に構成され、前記ピストン側係合部の内周面には、Ｕ字状係合溝が設けられ、前記ロッド側係合部は、前記Ｕ字状係合溝に挿入された環状の係合突起を有してもよい。 The piston-side engagement portion bulges in the axial direction from the end surface of the piston body and is configured in a U-shape when viewed from the axial direction. A U-shaped engagement is formed on the inner peripheral surface of the piston-side engagement portion. A mating groove may be provided, and the rod-side engagement portion may have an annular engagement protrusion inserted into the U-shaped engagement groove.
　前記ピストンロッドの外周部に配置され、ストロークエンド到達時の衝撃を緩和するリング状の外周側ダンパと、前記ピストン本体と前記外周側ダンパとの間に介装されたリング状のスペーサとを備え、前記ピストン本体、前記スペーサ及び前記外周側ダンパは軸方向に積層されている。 A ring-shaped outer peripheral damper disposed on the outer peripheral portion of the piston rod for reducing the impact when reaching the stroke end, and a ring-shaped spacer interposed between the piston main body and the outer peripheral damper. The piston main body, the spacer, and the outer peripheral damper are stacked in the axial direction.
　また、本発明は、内部に摺動孔を有するボディと、前記摺動孔に沿って往復移動可能に配置されたピストン組立体とを備えた流体圧装置であって、前記ピストン組立体は、前記摺動孔内を軸方向に変位可能なピストン本体と、前記ピストン本体から軸方向に突出したピストンロッドとを備え、前記ピストン本体は、ピストン側係合部を有し、前記ピストンロッドは、前記ピストン側係合部に係合したロッド側係合部を有し、前記ピストン側係合部と前記ロッド側係合部は、一方の係合部が他方の係合部に側方から挿入されることにより、前記ピストン本体と前記ピストンロッドとの軸方向の相対変位を規制するように係合していることを特徴とする。 Further, the present invention is a fluid pressure device including a body having a sliding hole inside, and a piston assembly arranged to be reciprocally movable along the sliding hole, wherein the piston assembly includes: A piston main body that is axially displaceable in the sliding hole, and a piston rod that protrudes axially from the piston main body, the piston main body has a piston-side engagement portion, and the piston rod is It has a rod side engaging part engaged with the piston side engaging part, and one engaging part of the piston side engaging part and the rod side engaging part is inserted into the other engaging part from the side. Thus, the piston main body and the piston rod are engaged so as to restrict relative displacement in the axial direction.
　前記流体圧装置は、流体圧シリンダ、バルブ装置、測長シリンダ、スライドテーブル又はチャック装置として構成されていてもよい。 The fluid pressure device may be configured as a fluid pressure cylinder, a valve device, a length measuring cylinder, a slide table, or a chuck device.
　本発明のピストン組立体及び流体圧装置によれば、ピストン本体とピストンロッドとを接続する組立工程において、ピストン側係合部とロッド側係合部とを、ピストン本体の軸に対して垂直な方向に変位させて係合させることにより、ピストン本体とピストンロッドとを簡単に接続することができる。また、この組立ては、専用工具や設備や装置を用いることなく手作業で簡単に行うことができる。従って、本発明のピストン組立体によれば、組立作業を簡素化することができる。 According to the piston assembly and the fluid pressure device of the present invention, in the assembly step of connecting the piston body and the piston rod, the piston side engagement portion and the rod side engagement portion are perpendicular to the axis of the piston body. The piston body and the piston rod can be easily connected by being displaced in the direction and engaged. Further, this assembly can be easily performed manually without using a dedicated tool, equipment or device. Therefore, according to the piston assembly of the present invention, the assembly work can be simplified.
　添付した図面と協同する次の好適な実施の形態例の説明から、上記の目的、特徴及び利点がより明らかとなるだろう。 The above objects, features and advantages will become more apparent from the following description of preferred embodiments in conjunction with the accompanying drawings.
図１は、第１実施形態に係るピストン組立体を備えた流体圧シリンダの断面図である。FIG. 1 is a cross-sectional view of a fluid pressure cylinder including a piston assembly according to a first embodiment. 図２は、ピストン組立体のピストン本体側からの斜視図である。FIG. 2 is a perspective view of the piston assembly from the piston body side. 図３は、ピストン組立体のピストンロッド側からの斜視図である。FIG. 3 is a perspective view of the piston assembly from the piston rod side. 図４Ａは、ピストン組立体の組立方法の第１説明図であり、図４Ｂは、ピストン組立体の組立方法の第２説明図であり、図４Ｃは、ピストン組立体の組立方法の第３説明図である。4A is a first explanatory view of a piston assembly method, FIG. 4B is a second explanatory view of the piston assembly method, and FIG. 4C is a third description of the piston assembly method. FIG. 図５は、第２実施形態に係るピストン組立体の断面図である。FIG. 5 is a cross-sectional view of the piston assembly according to the second embodiment. 図６は、第２実施形態に係るピストン組立体の斜視図である。FIG. 6 is a perspective view of the piston assembly according to the second embodiment. 図７は、第３実施形態に係るピストン組立体の断面図である。FIG. 7 is a cross-sectional view of the piston assembly according to the third embodiment. 図８Ａは、第４実施形態に係るピストン組立体の断面図であり、図８Ｂは、第５実施形態に係るピストン組立体の断面図である。FIG. 8A is a cross-sectional view of the piston assembly according to the fourth embodiment, and FIG. 8B is a cross-sectional view of the piston assembly according to the fifth embodiment. 図９Ａは、第６実施形態に係るピストン組立体の断面図であり、図９Ｂは、第７実施形態に係るピストン組立体の断面図である。FIG. 9A is a cross-sectional view of the piston assembly according to the sixth embodiment, and FIG. 9B is a cross-sectional view of the piston assembly according to the seventh embodiment. 図１０Ａは、第８実施形態に係るピストン組立体の断面図であり、図１０Ｂは、第９実施形態に係るピストン組立体の断面図である。FIG. 10A is a cross-sectional view of the piston assembly according to the eighth embodiment, and FIG. 10B is a cross-sectional view of the piston assembly according to the ninth embodiment. 図１１は、第１０実施形態に係るピストン組立体の断面図である。FIG. 11 is a cross-sectional view of the piston assembly according to the tenth embodiment. 図１２は、第１１実施形態に係るピストン組立体の断面図である。FIG. 12 is a cross-sectional view of the piston assembly according to the eleventh embodiment. 図１３は、第１２実施形態に係るピストン組立体を備えた流体圧シリンダの断面図である。FIG. 13 is a cross-sectional view of a fluid pressure cylinder including a piston assembly according to a twelfth embodiment. 図１４Ａは、単動型シリンダとして構成された流体圧シリンダの断面図であり、図１４Ｂは、単動型シリンダとして構成された別の流体圧シリンダの断面図である。FIG. 14A is a cross-sectional view of a fluid pressure cylinder configured as a single-acting cylinder, and FIG. 14B is a cross-sectional view of another fluid pressure cylinder configured as a single-acting cylinder. 図１５は、第１３実施形態に係るピストン組立体の断面図である。FIG. 15 is a sectional view of a piston assembly according to a thirteenth embodiment. 図１６は、図１５に示したピストン組立体のピストンロッド側からの斜視図である。16 is a perspective view from the piston rod side of the piston assembly shown in FIG.
　以下、本発明に係るピストン組立体及び流体圧装置について好適な実施形態を挙げ、添付の図面を参照しながら説明する。 Hereinafter, preferred embodiments of the piston assembly and the fluid pressure device according to the present invention will be described with reference to the accompanying drawings.
　流体圧装置の一例として図１に示す流体圧シリンダ１０Ａは、中空筒状のシリンダチューブ１２（ボディ）と、シリンダチューブ１２の一端部に配置されたヘッドカバー１４と、シリンダチューブ１２の他端部に配置されたロッドカバー１６と、シリンダチューブ１２の軸方向に沿って往復移動可能に配置されたピストン組立体１７Ａとを備える。 As an example of a fluid pressure device, a fluid pressure cylinder 10 </ b> A shown in FIG. 1 includes a hollow cylindrical cylinder tube 12 (body), a head cover 14 disposed at one end of the cylinder tube 12, and the other end of the cylinder tube 12. A rod cover 16 disposed and a piston assembly 17A disposed so as to be reciprocally movable along the axial direction of the cylinder tube 12 are provided.
　ピストン組立体１７Ａは、シリンダチューブ１２内に軸方向（矢印Ｘ方向）に移動可能に配置されたピストンユニット１８と、ピストンユニット１８に連結されたピストンロッド２０とを有する。この流体圧シリンダ１０Ａは、例えばワークの搬送等のためのアクチュエータとして用いられる。 The piston assembly 17 </ b> A includes a piston unit 18 that is arranged in the cylinder tube 12 so as to be movable in the axial direction (arrow X direction), and a piston rod 20 that is connected to the piston unit 18. The fluid pressure cylinder 10A is used as an actuator for conveying a workpiece, for example.
　シリンダチューブ１２は、例えば、アルミニウム合金等の金属材料により構成され、軸方向に沿って延在した筒体からなる。本実施形態では、シリンダチューブ１２は、中空円筒形に形成されている。シリンダチューブ１２は、軸方向の一端側（矢印Ｘ２方向側）に設けられた第１ポート１２ａと、軸方向の他端側（矢印Ｘ１方向側）に設けられた第２ポート１２ｂと、第１ポート１２ａ及び第２ポート１２ｂに連通する摺動孔１３（シリンダ室）とを有する。 The cylinder tube 12 is made of, for example, a metal material such as an aluminum alloy, and includes a cylinder that extends along the axial direction. In the present embodiment, the cylinder tube 12 is formed in a hollow cylindrical shape. The cylinder tube 12 includes a first port 12a provided on one end side in the axial direction (arrow X2 direction side), a second port 12b provided on the other end side in the axial direction (arrow X1 direction side), and a first A sliding hole 13 (cylinder chamber) communicating with the port 12a and the second port 12b is provided.
　ヘッドカバー１４は、例えば、シリンダチューブ１２と同様の金属材料により構成された板状体であり、シリンダチューブ１２の一端部（矢印Ｘ２方向側の端部）を閉塞するように設けられている。ヘッドカバー１４により、シリンダチューブ１２の一端部が気密に閉じられている。 The head cover 14 is, for example, a plate-like body made of the same metal material as the cylinder tube 12, and is provided so as to close one end portion (end portion on the arrow X2 direction side) of the cylinder tube 12. One end of the cylinder tube 12 is hermetically closed by the head cover 14.
　ロッドカバー１６は、例えば、シリンダチューブ１２と同様の金属材料により構成された円形リング状の部材であり、シリンダチューブ１２の他端部（矢印Ｘ１方向側の端部）を閉塞するように設けられている。ロッドカバー１６の外周部には外側環状溝２４が形成されている。外側環状溝２４には、ロッドカバー１６の外周面と摺動孔１３の内周面との間をシールする弾性材料からなる外側シール部材２６が装着されている。 The rod cover 16 is, for example, a circular ring-shaped member made of the same metal material as the cylinder tube 12, and is provided so as to close the other end (the end on the arrow X1 direction side) of the cylinder tube 12. ing. An outer annular groove 24 is formed on the outer periphery of the rod cover 16. An outer seal member 26 made of an elastic material that seals between the outer peripheral surface of the rod cover 16 and the inner peripheral surface of the sliding hole 13 is attached to the outer annular groove 24.
　ロッドカバー１６の内周部には内側環状溝２８が形成されている。内側環状溝２８には、ロッドカバー１６の内周面とピストンロッド２０の外周面との間をシールする弾性材料からなる内側シール部材３０が装着されている。なお、ロッドカバー１６は、シリンダチューブ１２の他端側の内周部に固定されたストッパ３２により係止されている。 An inner annular groove 28 is formed on the inner periphery of the rod cover 16. An inner seal member 30 made of an elastic material that seals between the inner peripheral surface of the rod cover 16 and the outer peripheral surface of the piston rod 20 is attached to the inner annular groove 28. The rod cover 16 is locked by a stopper 32 fixed to the inner peripheral portion on the other end side of the cylinder tube 12.
　ピストンユニット１８は、シリンダチューブ１２内（摺動孔１３）に軸方向に摺動可能に収容され、摺動孔１３内を第１ポート１２ａ側の第１圧力室１３ａと第２ポート１２ｂ側の第２圧力室１３ｂとに仕切っている。本実施形態において、ピストンユニット１８は、ピストンロッド２０の一端部２０ａ（以下、「基端部２０ａ」という）に連結されている。 The piston unit 18 is accommodated in the cylinder tube 12 (sliding hole 13) so as to be slidable in the axial direction, and the first pressure chamber 13a on the first port 12a side and the second port 12b side in the sliding hole 13 are accommodated. It is partitioned off from the second pressure chamber 13b. In the present embodiment, the piston unit 18 is connected to one end 20 a (hereinafter referred to as “base end 20 a”) of the piston rod 20.
　図１に示すように、ピストンユニット１８は、ピストンロッド２０に接続されたピストン本体３８と、ピストン本体３８に取り付けられたパッキン３４及びマグネット４８とを有する。 As shown in FIG. 1, the piston unit 18 includes a piston main body 38 connected to the piston rod 20, and a packing 34 and a magnet 48 attached to the piston main body 38.
　ピストン本体３８は、ピストンロッド２０の基端部２０ａから径方向外側に突出した環状の部材である。ピストン本体３８の外径は、ピストンロッド２０の外径よりも大きい。ピストン本体３８の中心部には、軸方向に貫通した貫通孔３８ａが設けられている。ピストン本体３８の外周部（以下、「ピストン外周部３８ｂ」という）には、環状のパッキン装着溝３６及び環状のマグネット装着溝４９が軸方向に間隔を置いて設けられている。 The piston main body 38 is an annular member that protrudes radially outward from the base end portion 20a of the piston rod 20. The outer diameter of the piston body 38 is larger than the outer diameter of the piston rod 20. A through hole 38 a penetrating in the axial direction is provided at the center of the piston main body 38. An annular packing mounting groove 36 and an annular magnet mounting groove 49 are provided in the outer peripheral portion of the piston main body 38 (hereinafter referred to as “piston outer peripheral portion 38 b”) with an interval in the axial direction.
　ピストン本体３８には、ピストンロッド２０の後述するロッド側係合部４２と係合するピストン側係合部４０が設けられている。ピストン側係合部４０は、側方に開口した形状を有する。図３において、ピストン側係合部４０は、貫通孔３８ａを囲む円盤状壁部３８ｃから軸方向に突出するとともに、貫通孔３８ａを部分的に囲む半円弧状に形成されている。 The piston main body 38 is provided with a piston side engaging portion 40 that engages with a rod side engaging portion 42 described later of the piston rod 20. The piston side engaging part 40 has a shape opened to the side. In FIG. 3, the piston-side engaging portion 40 is formed in a semicircular arc shape that protrudes in the axial direction from a disk-like wall portion 38 c surrounding the through hole 38 a and partially surrounds the through hole 38 a.
　図１に示すように、ピストン側係合部４０の内周部には係合溝４４が設けられている。係合溝４４は、ピストン側係合部４０と同様に半円弧状に延在している。係合溝４４に隣接して、内方に突出した内方突起４５が設けられている。ピストン側係合部４０（係合溝４４）は、半円弧状に限らず、Ｃ字状又はＵ字状に形成されてもよい。 As shown in FIG. 1, an engagement groove 44 is provided in the inner peripheral portion of the piston side engagement portion 40. The engagement groove 44 extends in a semicircular arc shape as in the piston-side engagement portion 40. An inward protrusion 45 that protrudes inward is provided adjacent to the engagement groove 44. The piston side engaging portion 40 (engaging groove 44) is not limited to a semicircular arc shape, and may be formed in a C shape or a U shape.
　ピストン本体３８には、ピストン側係合部４０を囲むとともにピストン本体３８の軸方向に深さを有する肉抜き部４６が設けられている。図１及び図３において、肉抜き部４６は、ロッドカバー１６側に開口する環状に形成されるとともに、ピストン側係合部４０とマグネット装着溝４９との間に設けられている。なお、肉抜き部４６は、周方向に間隔を置いて設けられた複数の穴により構成されてもよい。肉抜き部４６は設けられなくてもよい。 The piston body 38 is provided with a lightening portion 46 that surrounds the piston-side engagement portion 40 and has a depth in the axial direction of the piston body 38. 1 and 3, the lightening portion 46 is formed in an annular shape that opens to the rod cover 16 side, and is provided between the piston-side engaging portion 40 and the magnet mounting groove 49. Note that the lightening portion 46 may be configured by a plurality of holes provided at intervals in the circumferential direction. The meat removal part 46 does not need to be provided.
　図３において、マグネット装着溝４９の底部を形成する周壁４９ａには、周方向に延びる孔部５０が設けられている。孔部５０は、ピストン側係合部４０の側方開口に対向する位置に設けられ、周壁４９ａを厚さ方向に貫通している。周壁４９ａには、孔部５０に連通する切欠部５２が設けられている。切欠部５２は、周壁４９ａの内周部を部分的に切り欠いた円弧形状を有する。詳細は後述するが、孔部５０及び切欠部５２は、ピストン本体３８へのピストンロッド２０の組み付け時に利用される。 In FIG. 3, the peripheral wall 49a that forms the bottom of the magnet mounting groove 49 is provided with a hole 50 extending in the circumferential direction. The hole 50 is provided at a position facing the side opening of the piston side engaging portion 40 and penetrates the peripheral wall 49a in the thickness direction. The peripheral wall 49 a is provided with a notch 52 that communicates with the hole 50. The notch 52 has an arc shape obtained by partially notching the inner periphery of the peripheral wall 49a. Although details will be described later, the hole 50 and the notch 52 are used when the piston rod 20 is assembled to the piston body 38.
　図１及び図２において、ピストン本体３８のヘッドカバー１４側の面３８ｄには、ピストンロッド２０側に凹む肉抜き部５３が設けられている。肉抜き部５３は、環状に形成されるとともに、パッキン装着溝３６と貫通孔３８ａとの間に設けられている。なお、肉抜き部５３は、周方向に間隔を置いて設けられた複数の穴により構成されてもよい。肉抜き部５３は設けられなくてもよい。 1 and 2, a surface 38d on the head cover 14 side of the piston main body 38 is provided with a lightening portion 53 that is recessed toward the piston rod 20 side. The lightening portion 53 is formed in an annular shape and is provided between the packing mounting groove 36 and the through hole 38a. In addition, the lightening part 53 may be comprised by the some hole provided at intervals in the circumferential direction. The meat extraction part 53 does not need to be provided.
　ピストン本体３８は、硬質樹脂により構成されている。例えば、射出成形により、樹脂製のピストン本体３８を作製することができる。なお、ピストン本体３８は、樹脂製に限らず、例えば、炭素鋼、ステンレス鋼、アルミニウム合金等の金属材料により構成されてもよい。 The piston body 38 is made of hard resin. For example, the resin-made piston main body 38 can be manufactured by injection molding. The piston body 38 is not limited to resin, and may be made of a metal material such as carbon steel, stainless steel, or aluminum alloy.
　パッキン３４は、ピストン外周部３８ｂ（パッキン装着溝３６）に装着された弾性体からなる円環状シール部材（例えば、Ｏリング）である。パッキン３４の構成材料としては、ゴム材やエラストマー材等の弾性材料が挙げられる。パッキン３４は、その全周に亘って、摺動孔１３の内周面及びピストン外周部３８ｂ（パッキン装着溝３６）と気密又は液密に密着している。パッキン３４によりピストンユニット１８の外周面と摺動孔１３の内周面との間がシールされ、摺動孔１３内の第１圧力室１３ａと第２圧力室１３ｂが気密又は液密に仕切られている。 The packing 34 is an annular seal member (for example, an O-ring) made of an elastic body mounted on the piston outer peripheral portion 38b (packing mounting groove 36). Examples of the constituent material of the packing 34 include elastic materials such as rubber materials and elastomer materials. The packing 34 is in airtight or liquid tight contact with the inner peripheral surface of the sliding hole 13 and the piston outer peripheral portion 38b (packing mounting groove 36) over the entire circumference. The seal 34 seals between the outer peripheral surface of the piston unit 18 and the inner peripheral surface of the sliding hole 13, and the first pressure chamber 13a and the second pressure chamber 13b in the sliding hole 13 are partitioned in an airtight or liquid tight manner. ing.
　マグネット４８は、円形リング状の部材であり、ピストン外周部３８ｂ（マグネット装着溝４９）に装着されている。マグネット４８は、弾性変形可能に構成されている。マグネット４８は、プラスチックマグネットであり、周方向の一部にスリット５４（切れ目）が設けられている。このため、マグネット４８は、マグネット装着溝４９への装着に際して弾性変形することにより容易に装着が可能である。 The magnet 48 is a circular ring-shaped member, and is mounted on the piston outer peripheral portion 38b (magnet mounting groove 49). The magnet 48 is configured to be elastically deformable. The magnet 48 is a plastic magnet, and has a slit 54 (cut) in a part in the circumferential direction. For this reason, the magnet 48 can be easily mounted by being elastically deformed when mounted in the magnet mounting groove 49.
　なお、シリンダチューブ１２の外面には、ピストンユニット１８のストローク両端に相当する位置に図示しない磁気センサが取り付けられている。マグネット４８が発生する磁気を磁気センサによって感知することで、ピストンユニット１８の動作位置が検出される。 A magnetic sensor (not shown) is attached to the outer surface of the cylinder tube 12 at positions corresponding to both stroke ends of the piston unit 18. The operating position of the piston unit 18 is detected by sensing the magnetism generated by the magnet 48 with a magnetic sensor.
　ピストンロッド２０は、摺動孔１３の軸方向に沿って延在する柱状（円柱状）の部材である。ピストンロッド２０の基端部２０ａにピストン本体３８が接続されている。ピストンロッド２０の基端部２０ａには、ピストン側係合部４０に係合したロッド側係合部４２が設けられている。ピストン側係合部４０とロッド側係合部４２は、一方の係合部が他方の係合部に側方から挿入されることにより、ピストン本体３８とピストンロッド２０との軸方向の相対変位を規制するように係合している。 The piston rod 20 is a columnar (columnar) member extending along the axial direction of the sliding hole 13. A piston main body 38 is connected to the proximal end portion 20 a of the piston rod 20. A rod-side engagement portion 42 that is engaged with the piston-side engagement portion 40 is provided at the proximal end portion 20 a of the piston rod 20. The piston-side engaging portion 40 and the rod-side engaging portion 42 have an axial relative displacement between the piston main body 38 and the piston rod 20 by inserting one engaging portion into the other engaging portion from the side. It is engaged to regulate.
　ピストンロッド２０の軸方向に沿った断面において、ロッド側係合部４２は、Ｔ字状の形状を有する。具体的に、ロッド側係合部４２は、係合溝４４に挿入された環状の係合突起５６を有する。係合突起５６は、周方向に円環状に延在する。ピストンロッド２０の外周部には、係合突起５６に隣接して、周方向に円環状に延在する環状溝５８が設けられている。 In the cross section along the axial direction of the piston rod 20, the rod side engaging portion 42 has a T-shape. Specifically, the rod side engaging portion 42 has an annular engaging protrusion 56 inserted into the engaging groove 44. The engagement protrusion 56 extends in an annular shape in the circumferential direction. An annular groove 58 extending annularly in the circumferential direction is provided on the outer peripheral portion of the piston rod 20 adjacent to the engagement protrusion 56.
　図１に示すピストン組立体１７Ａの組立状態において、ロッド側係合部４２の係合突起５６がピストン側係合部４０の係合溝４４に挿入されており、ピストン側係合部４０の内方突起４５がロッド側係合部４２の環状溝５８に挿入されている。これにより、ピストン本体３８とピストンロッド２０とは軸方向の相対移動が阻止された状態で接続されている。従って、流体圧によるピストン本体３８の推力は、ピストンロッド２０に良好に伝達される。 In the assembled state of the piston assembly 17 </ b> A shown in FIG. 1, the engagement protrusion 56 of the rod side engagement portion 42 is inserted into the engagement groove 44 of the piston side engagement portion 40. The projection 45 is inserted into the annular groove 58 of the rod side engaging portion 42. Thereby, the piston main body 38 and the piston rod 20 are connected in a state where relative movement in the axial direction is prevented. Therefore, the thrust of the piston main body 38 due to the fluid pressure is satisfactorily transmitted to the piston rod 20.
　なお、ピストン側係合部４０の構造とロッド側係合部４２の構造を互いに置換してもよい。すなわち、ピストン側係合部４０が、上記係合突起５６を有する構造とされ、ロッド側係合部４２が、上記係合溝４４を有する構造とされてもよい。 Note that the structure of the piston side engaging portion 40 and the structure of the rod side engaging portion 42 may be replaced with each other. That is, the piston side engaging portion 40 may have a structure having the engaging protrusion 56, and the rod side engaging portion 42 may have a structure having the engaging groove 44.
　ピストン側係合部４０及びロッド側係合部４２は、ピストン本体３８の軸ａ１を中心に相対回転可能に係合している。従って、ピストン本体３８とピストンロッド２０とは、ピストン本体３８の軸ａ１を中心に相対回転可能である。 The piston side engaging portion 40 and the rod side engaging portion 42 are engaged with each other so as to be relatively rotatable about the axis a1 of the piston main body 38. Therefore, the piston main body 38 and the piston rod 20 are relatively rotatable around the axis a1 of the piston main body 38.
　ピストンロッド２０はロッドカバー１６を貫通している。ピストンロッド２０の基端部２０ａと反対側の端部である先端部２０ｂは、摺動孔１３の外部に露出している。ピストンロッド２０の構成材料としては、例えば、炭素鋼、ステンレス鋼、アルミニウム合金等の金属材料や、硬質樹脂等が挙げられる。 The piston rod 20 penetrates the rod cover 16. A distal end portion 20 b that is an end portion on the opposite side of the proximal end portion 20 a of the piston rod 20 is exposed to the outside of the sliding hole 13. Examples of the constituent material of the piston rod 20 include metal materials such as carbon steel, stainless steel, and aluminum alloy, and hard resin.
　ピストン組立体１７Ａは、ストロークエンド到達時の衝撃を緩和するダンパ機構６０を備える。図１～図３において、ダンパ機構６０は、ピストンロッド２０の外周部に配置された外周側ダンパ６２と、ピストンロッド２０の端面に配置された端部側ダンパ６４とを有する。外周側ダンパ６２及び端部側ダンパ６４は、例えば、ゴム材やエラストマー材等の弾性材料（ウレタンゴム等）により構成されている。 The piston assembly 17A includes a damper mechanism 60 that reduces the impact when the stroke end is reached. 1 to 3, the damper mechanism 60 includes an outer peripheral side damper 62 disposed on the outer peripheral portion of the piston rod 20 and an end portion side damper 64 disposed on the end surface of the piston rod 20. The outer peripheral side damper 62 and the end side damper 64 are made of an elastic material (urethane rubber or the like) such as a rubber material or an elastomer material, for example.
　外周側ダンパ６２は、ロッドカバー１６側のストロークエンド到達時の衝撃を緩和する。外周側ダンパ６２は、ピストン本体３８よりもロッドカバー１６側で、ピストン本体３８の近傍箇所に配置されている。外周側ダンパ６２は、円環状に形成されており、ピストンロッド２０を囲むように配置されている。 The outer periphery side damper 62 alleviates the impact when reaching the stroke end on the rod cover 16 side. The outer periphery side damper 62 is disposed on the rod cover 16 side of the piston body 38 and in the vicinity of the piston body 38. The outer periphery side damper 62 is formed in an annular shape and is disposed so as to surround the piston rod 20.
　ピストンロッド２０の外周部には、ピストン本体３８の近傍箇所に、円環状のストッパ装着溝７０が設けられている。ストッパ装着溝７０に、円環状のストッパ部材７２が装着されている。ストッパ部材７２は、周方向に分割された複数のストッパ要素７２ａにより構成される。各ストッパ要素７２ａは、弧状に形成されている。 An annular stopper mounting groove 70 is provided in the vicinity of the piston main body 38 on the outer periphery of the piston rod 20. An annular stopper member 72 is mounted in the stopper mounting groove 70. The stopper member 72 includes a plurality of stopper elements 72a divided in the circumferential direction. Each stopper element 72a is formed in an arc shape.
　図２及び図３において、ストッパ部材７２は、半割り構造となっており、２つの半円弧状のストッパ要素７２ａからなる。ストッパ部材７２の内周部（ストッパ要素７２ａの内周部）が、ストッパ装着溝７０に挿入されている。ストッパ部材７２は、硬質材料、例えば、上述したピストンロッド２０と同様の材料により構成される。 2 and 3, the stopper member 72 has a half structure, and is composed of two half-arc shaped stopper elements 72a. The inner peripheral portion of the stopper member 72 (the inner peripheral portion of the stopper element 72 a) is inserted into the stopper mounting groove 70. The stopper member 72 is made of a hard material, for example, the same material as the piston rod 20 described above.
　外周側ダンパ６２は、ストッパ部材７２を覆って、当該ストッパ部材７２に装着されている。具体的には、外周側ダンパ６２は、ストッパ部材７２のロッドカバー１６側（矢印Ｘ１方向側）を覆うダンパ本体部６２ａと、ストッパ部材７２の外周部を覆う外周被覆部６２ｂとを有する。外周被覆部６２ｂがストッパ部材７２の外周部に装着されている。これにより、外周側ダンパ６２は、ストッパ部材７２によって支持されている。また、ストッパ部材７２に外周側ダンパ６２が装着されることで、ストッパ部材７２は、ストッパ装着溝７０から離脱することが阻止されている。 The outer periphery side damper 62 covers the stopper member 72 and is attached to the stopper member 72. Specifically, the outer peripheral damper 62 includes a damper main body 62 a that covers the rod cover 16 side (arrow X1 direction side) of the stopper member 72, and an outer peripheral covering portion 62 b that covers the outer peripheral portion of the stopper member 72. An outer peripheral covering portion 62 b is attached to the outer peripheral portion of the stopper member 72. Thereby, the outer periphery side damper 62 is supported by the stopper member 72. Further, since the outer peripheral damper 62 is mounted on the stopper member 72, the stopper member 72 is prevented from being detached from the stopper mounting groove 70.
　端部側ダンパ６４は、ヘッドカバー１４側のストロークエンド到達時の衝撃を緩和する。端部側ダンパ６４は、ピストン本体３８とピストンロッド２０との間に保持されるとともに、ピストン本体３８の中心部に設けられた貫通孔３８ａから突出している。図１において、端部側ダンパ６４は、ピストン本体３８のヘッドカバー１４側の面３８ｄよりもヘッドカバー１４側（矢印Ｘ２方向側）に突出している。 The end side damper 64 reduces the impact when the head end of the head cover 14 is reached. The end-side damper 64 is held between the piston main body 38 and the piston rod 20 and protrudes from a through hole 38 a provided in the center of the piston main body 38. In FIG. 1, the end side damper 64 protrudes to the head cover 14 side (arrow X2 direction side) from the surface 38d of the piston main body 38 on the head cover 14 side.
　なお、端部側ダンパ６４の突出端面は、ピストン本体３８のヘッドカバー１４側の端面よりもロッドカバー１６側に位置していてもよいが、この場合には、ヘッドカバー１４に、ピストン組立体１７Ａ側に突出する突起が設けられる。 The protruding end surface of the end side damper 64 may be positioned closer to the rod cover 16 than the end surface of the piston main body 38 on the head cover 14 side. In this case, the piston cover 17A side is disposed on the head cover 14. Protrusions that protrude from the surface are provided.
　図２及び図３において、端部側ダンパ６４は、円筒形状（又は円盤形状）を有する。具体的に、端部側ダンパ６４のピストンロッド２０側の端部には、径方向外側に突出した環状の鍔部６４ａが設けられている。図１において、鍔部６４ａは、ピストン本体３８の内周部に設けられた段差部３８ｅ（縮径部）と、ピストンロッド２０の端面２０ｃとの間に保持されている。 2 and 3, the end side damper 64 has a cylindrical shape (or a disk shape). Specifically, an end portion of the end portion side damper 64 on the piston rod 20 side is provided with an annular flange portion 64a that protrudes radially outward. In FIG. 1, the flange portion 64 a is held between a stepped portion 38 e (reduced diameter portion) provided on the inner peripheral portion of the piston main body 38 and the end surface 20 c of the piston rod 20.
　図１において、端部側ダンパ６４は、ピストン本体３８の内周部及びピストンロッド２０の端面２０ｃと密着しており、これにより、ピストン本体３８とピストンロッド２０との間を気密又は液密にシールしている。 In FIG. 1, the end side damper 64 is in close contact with the inner peripheral portion of the piston main body 38 and the end surface 20 c of the piston rod 20, so that the space between the piston main body 38 and the piston rod 20 is airtight or liquid tight. It is sealed.
　端部側ダンパ６４の鍔部６４ａが設けられた側の端部は、組立前の状態（ピストンロッド２０とピストン本体３８との間に保持される前の状態）で、軸方向に膨出した膨出部６４ｂ（図１の仮想線を参照）を有する。これにより、端部側ダンパ６４は、組立状態（ピストンロッド２０とピストン本体３８との間に保持された状態）でピストンロッド２０の端面２０ｃを弾性的に押圧している。このため、ピストンロッド２０とピストン本体３８とのガタツキが抑制されている。 The end of the end side damper 64 on the side where the flange 64a is provided bulges in the axial direction in a state before assembly (a state before being held between the piston rod 20 and the piston main body 38). It has the bulging part 64b (refer the virtual line of FIG. 1). Thereby, the end side damper 64 elastically presses the end surface 20c of the piston rod 20 in an assembled state (a state held between the piston rod 20 and the piston main body 38). For this reason, rattling between the piston rod 20 and the piston body 38 is suppressed.
　なお、流体圧シリンダ１０Ａにおいて、外周側ダンパ６２及び端部側ダンパ６４のいずれか一方をなくしてもよく、あるいは、外周側ダンパ６２及び端部側ダンパ６４の両方をなくしてもよい。 In the fluid pressure cylinder 10A, either the outer peripheral side damper 62 or the end side damper 64 may be omitted, or both the outer peripheral side damper 62 and the end side damper 64 may be omitted.
　次に、上記のように構成されるピストン組立体１７Ａの組立方法の一例を説明する。 Next, an example of an assembly method for the piston assembly 17A configured as described above will be described.
　まず、図４Ａのように、ピストン本体３８、ピストンロッド２０及び端部側ダンパ６４を用意する。次に、ピストン側係合部４０が設けられた側からピストン本体３８の貫通孔３８ａに端部側ダンパ６４を挿入する。そして、ピストン本体３８とピストンロッド２０とを軸方向に相対変位させて、図４Ｂのように、ピストンロッド２０の基端部２０ａ（ピストン側係合部４０）を、ピストン側係合部４０とピストン外周部３８ｂとの間（肉抜き部４６）に挿入する。 First, as shown in FIG. 4A, a piston main body 38, a piston rod 20, and an end side damper 64 are prepared. Next, the end side damper 64 is inserted into the through hole 38a of the piston main body 38 from the side where the piston side engaging portion 40 is provided. Then, the piston main body 38 and the piston rod 20 are relatively displaced in the axial direction, and the base end portion 20a (piston side engaging portion 40) of the piston rod 20 is replaced with the piston side engaging portion 40 as shown in FIG. 4B. It inserts between piston outer peripheral parts 38b (thickening part 46).
　この場合、ピストン本体３８の切欠部５２が、ピストンロッド２０の係合突起５６の通過を許容するとともに、孔部５０が係合突起５６の周方向の一部を受け入れる。すなわち、係合突起５６の周方向の一部が、ピストン本体３８の切欠部５２を通過するとともに孔部５０に挿入される。このように切欠部５２及び孔部５０は、ピストンロッド２０の係合突起５６がピストン外周部３８ｂと干渉することを避けるための逃げ部として機能する。 In this case, the notch 52 of the piston main body 38 allows the engagement protrusion 56 of the piston rod 20 to pass, and the hole 50 receives a part of the engagement protrusion 56 in the circumferential direction. That is, a part of the engagement protrusion 56 in the circumferential direction passes through the notch 52 of the piston main body 38 and is inserted into the hole 50. Thus, the notch 52 and the hole 50 function as escape portions for avoiding the engagement protrusion 56 of the piston rod 20 from interfering with the piston outer peripheral portion 38b.
　図４Ｂにおいて、ピストン本体３８の軸ａ１とピストンロッド２０の軸ａ２とは互いにずれており、ロッド側係合部４２は、ピストン側係合部４０の側方に位置している。そこで、図４Ｃのように、ピストン本体３８の軸ａ１とピストンロッド２０の軸ａ２とを一致させるように、ピストン本体３８の軸ａ１と垂直な方向に、ピストン本体３８とピストンロッド２０とを相対移動させて、係合突起５６を係合溝４４に挿入する。これにより、ピストン側係合部４０とロッド側係合部４２とが係合状態となり、ピストン本体３８とピストンロッド２０とが接続された状態となる。 4B, the axis a1 of the piston main body 38 and the axis a2 of the piston rod 20 are shifted from each other, and the rod side engaging portion 42 is located on the side of the piston side engaging portion 40. Therefore, as shown in FIG. 4C, the piston main body 38 and the piston rod 20 are moved relative to each other in a direction perpendicular to the axis a1 of the piston main body 38 so that the axis a1 of the piston main body 38 and the axis a2 of the piston rod 20 coincide. The engagement protrusion 56 is inserted into the engagement groove 44 by being moved. Thereby, the piston side engaging part 40 and the rod side engaging part 42 will be in an engaged state, and the piston main body 38 and the piston rod 20 will be in the connected state.
　次に、ピストン本体３８にパッキン３４及びマグネット４８を装着するとともに、ストッパ部材７２及び外周側ダンパ６２をピストンロッド２０に装着する。なお、ピストン本体３８へのパッキン３４及びマグネット４８の装着は、ピストン本体３８への端部側ダンパ６４及びピストンロッド２０の装着前に行ってもよい。 Next, the packing 34 and the magnet 48 are mounted on the piston main body 38, and the stopper member 72 and the outer circumferential damper 62 are mounted on the piston rod 20. The packing 34 and the magnet 48 may be attached to the piston main body 38 before the end side damper 64 and the piston rod 20 are attached to the piston main body 38.
　ピストンロッド２０へのストッパ部材７２及び外周側ダンパ６２の装着に際しては、まず、環状のストッパ部材７２を形成するように、ピストンロッド２０のストッパ装着溝７０に２つのストッパ要素７２ａを個別に装着する（嵌め込む）。次に、ピストンロッド２０の先端部２０ｂ側から基端部２０ａ側に向かって外周側ダンパ６２を移動させて、外周側ダンパ６２をストッパ部材７２（２つのストッパ要素７２ａ）に被せる。これにより、ストッパ部材７２がストッパ装着溝７０から離脱することが阻止されるとともに、ピストンロッド２０の外周部の所定位置に外周側ダンパ６２が保持される。 When mounting the stopper member 72 and the outer circumferential damper 62 to the piston rod 20, first, the two stopper elements 72a are individually mounted in the stopper mounting groove 70 of the piston rod 20 so as to form the annular stopper member 72. (Fit). Next, the outer circumferential damper 62 is moved from the distal end portion 20b side of the piston rod 20 toward the proximal end portion 20a side, and the outer circumferential damper 62 is placed on the stopper member 72 (two stopper elements 72a). Accordingly, the stopper member 72 is prevented from being detached from the stopper mounting groove 70, and the outer peripheral side damper 62 is held at a predetermined position on the outer peripheral portion of the piston rod 20.
　以上により、図１に示したピストン組立体１７Ａが得られる。図１のようにピストン組立体１７Ａが流体圧シリンダ１０Ａに組み込まれた状態では、ピストン本体３８を含むピストンユニット１８はシリンダチューブ１２によって支持され、ピストンロッド２０はロッドカバー１６によって支持される。このため、ピストン本体３８の軸ａ１とピストンロッド２０の軸ａ２とが一致した状態が維持される。従って、ピストン側係合部４０とロッド側係合部４２との係合は維持される。 Thus, the piston assembly 17A shown in FIG. 1 is obtained. In the state where the piston assembly 17 </ b> A is incorporated in the fluid pressure cylinder 10 </ b> A as shown in FIG. 1, the piston unit 18 including the piston body 38 is supported by the cylinder tube 12, and the piston rod 20 is supported by the rod cover 16. For this reason, the state where the axis a1 of the piston main body 38 and the axis a2 of the piston rod 20 coincide with each other is maintained. Therefore, the engagement between the piston side engaging portion 40 and the rod side engaging portion 42 is maintained.
　次に、上記のように構成された図１に示す流体圧シリンダ１０Ａの作用及び効果を説明する。流体圧シリンダ１０Ａは、第１ポート１２ａ又は第２ポート１２ｂを介して導入される圧力流体（例えば、圧縮空気）の作用によって、ピストンユニット１８を摺動孔１３内で軸方向に移動させる。これにより、当該ピストンユニット１８に連結されたピストンロッド２０が進退移動する。 Next, the operation and effect of the fluid pressure cylinder 10A shown in FIG. 1 configured as described above will be described. The fluid pressure cylinder 10A moves the piston unit 18 in the axial direction in the sliding hole 13 by the action of the pressure fluid (for example, compressed air) introduced through the first port 12a or the second port 12b. Thereby, the piston rod 20 connected to the piston unit 18 moves forward and backward.
　具体的に、ピストンユニット１８をロッドカバー１６側へと変位（前進）させるには、第２ポート１２ｂを大気開放状態とし、図示しない圧力流体供給源から第１ポート１２ａを介して圧力流体を第１圧力室１３ａへと供給する。そうすると、圧力流体によってピストンユニット１８がロッドカバー１６側へと押される。これにより、ピストンユニット１８がピストンロッド２０とともにロッドカバー１６側へと変位（前進）する。 Specifically, in order to displace (advance) the piston unit 18 toward the rod cover 16, the second port 12b is opened to the atmosphere, and pressure fluid is supplied from a pressure fluid supply source (not shown) through the first port 12a. One pressure chamber 13a is supplied. Then, the piston unit 18 is pushed toward the rod cover 16 by the pressure fluid. Thereby, the piston unit 18 is displaced (advanced) together with the piston rod 20 toward the rod cover 16 side.
　そして、外周側ダンパ６２がロッドカバー１６の端面に当接することで、ピストンユニット１８の前進動作が停止する。この場合、弾性材料で構成された外周側ダンパ６２により、ピストン本体３８とロッドカバー１６とが直接当接することが回避される。これにより、ピストン本体３８が前進位置（ロッドカバー１６側のストロークエンド）へと到達することに伴う衝撃及び衝撃音の発生を効果的に防止又は抑制することができる。 The forward movement of the piston unit 18 is stopped when the outer circumferential damper 62 contacts the end face of the rod cover 16. In this case, the piston body 38 and the rod cover 16 are prevented from coming into direct contact with each other by the outer peripheral damper 62 made of an elastic material. Thereby, it is possible to effectively prevent or suppress the generation of impact and impact sound associated with the piston main body 38 reaching the forward position (stroke end on the rod cover 16 side).
　一方、ピストンユニット１８をヘッドカバー１４側へと変位（後退）させるには、第１ポート１２ａを大気開放状態とし、図示しない圧力流体供給源から第２ポート１２ｂを介して圧力流体を第２圧力室１３ｂへと供給する。そうすると、圧力流体によってピストンユニット１８がヘッドカバー１４側へと押される。これにより、ピストンユニット１８がヘッドカバー１４側へと変位する。 On the other hand, in order to displace (retreat) the piston unit 18 toward the head cover 14, the first port 12a is opened to the atmosphere, and pressure fluid is supplied from a pressure fluid supply source (not shown) through the second port 12b to the second pressure chamber. 13b. Then, the piston unit 18 is pushed toward the head cover 14 by the pressure fluid. As a result, the piston unit 18 is displaced toward the head cover 14 side.
　そして、端部側ダンパ６４の端面６４ｃがヘッドカバー１４に当接することで、ピストンユニット１８の後退動作が停止する。この場合、弾性材料で構成された端部側ダンパ６４により、ピストン本体３８とヘッドカバー１４とが直接当接することが回避される。これにより、ピストンユニット１８が後退位置（ヘッドカバー１４側のストロークエンド）へと到達することに伴う衝撃及び衝撃音の発生を効果的に防止又は抑制することができる。 Then, when the end surface 64c of the end side damper 64 comes into contact with the head cover 14, the retreating operation of the piston unit 18 is stopped. In this case, it is avoided that the piston main body 38 and the head cover 14 contact | abut directly by the edge part side damper 64 comprised with the elastic material. Thereby, it is possible to effectively prevent or suppress the generation of impact and impact sound associated with the piston unit 18 reaching the retracted position (stroke end on the head cover 14 side).
　この場合、本実施形態に係るピストン組立体１７Ａでは、ピストン本体３８は、ピストン側係合部４０を有し、ピストンロッド２０は、ピストン側係合部４０に係合したロッド側係合部４２を有する。そして、ピストン側係合部４０とロッド側係合部４２は、一方の係合部が他方の係合部に側方から挿入されることにより、ピストン本体３８とピストンロッド２０との軸方向の相対変位を規制するように係合している。 In this case, in the piston assembly 17 </ b> A according to the present embodiment, the piston main body 38 has the piston side engaging portion 40, and the piston rod 20 is engaged with the piston side engaging portion 40. Have The piston-side engaging portion 40 and the rod-side engaging portion 42 are inserted in the axial direction between the piston main body 38 and the piston rod 20 by inserting one engaging portion into the other engaging portion from the side. Engages so as to regulate relative displacement.
　このため、ピストン本体３８とピストンロッド２０とを接続する組立工程において、ピストン側係合部４０とロッド側係合部４２とを、ピストン本体３８の軸ａ１に対して垂直な方向に変位させて係合させることにより、ピストン本体３８とピストンロッド２０とを簡単に接続することができる。また、この組立ては、専用工具や設備や装置を用いることなく手作業で簡単に行うことができる。従って、本発明のピストン組立体１７Ａによれば、組立作業を簡素化することができる。 For this reason, in the assembly process for connecting the piston main body 38 and the piston rod 20, the piston side engaging portion 40 and the rod side engaging portion 42 are displaced in a direction perpendicular to the axis a1 of the piston main body 38. By engaging, the piston body 38 and the piston rod 20 can be easily connected. Further, this assembly can be easily performed manually without using a dedicated tool, equipment or device. Therefore, according to the piston assembly 17A of the present invention, the assembly work can be simplified.
　本実施形態では、ピストン側係合部４０及びロッド側係合部４２の一方の係合部は、Ｕ字状、Ｃ字状又は半円弧状の係合溝４４を有し、ピストン側係合部４０及びロッド側係合部４２の他方の係合部は、係合溝４４に挿入された環状の係合突起５６を有する。このため、一方の係合部が他方の係合部に側方から挿入されることにより、ピストン本体３８とピストンロッド２０との軸方向の相対変位を規制するように係合する構造を、簡素な構成で実現することができる。またこの構造によれば、ピストン本体３８とピストンロッド２０との十分な軸方向接続強度が得られる。 In the present embodiment, one of the piston-side engagement portion 40 and the rod-side engagement portion 42 has a U-shaped, C-shaped, or semicircular arc-shaped engagement groove 44, and the piston-side engagement The other engaging portion of the portion 40 and the rod side engaging portion 42 has an annular engaging protrusion 56 inserted into the engaging groove 44. For this reason, the structure which engages so that the relative displacement of the axial direction of the piston main body 38 and the piston rod 20 may be controlled simply by inserting one engaging part into the other engaging part from the side. Can be realized with a simple configuration. Further, according to this structure, a sufficient axial connection strength between the piston main body 38 and the piston rod 20 can be obtained.
　本実施形態では、ピストン側係合部４０及びロッド側係合部４２は、ピストン本体３８の軸ａ１を中心に相対回転可能に係合している。このため、設備への流体圧シリンダ１０Ａの据え付けの際に、ピストンロッド２０を容易に回転させることができ、便利である。また、ピストンロッド２０が回転可能である点は、後述する多角形のピストン本体３８Ａを備えたピストン組立体１７Ｂ（図５及び図６）についても同様である。 In the present embodiment, the piston-side engagement portion 40 and the rod-side engagement portion 42 are engaged with each other so as to be relatively rotatable about the axis a1 of the piston body 38. For this reason, the piston rod 20 can be easily rotated when the fluid pressure cylinder 10A is installed in the facility, which is convenient. The piston rod 20 can be rotated in the same manner for a piston assembly 17B (FIGS. 5 and 6) including a polygonal piston main body 38A described later.
　本実施形態では、ストロークエンド到達時の衝撃を緩和するダンパ機構６０を備え、ダンパ機構６０は、ストロークエンド到達時にピストン本体３８に衝撃荷重を伝達しないようにピストン本体３８に支持されている。このため、ピストン本体３８は、作動流体からの圧力に耐えられる程度の強度を持つように設計されていればよく、樹脂製とすることが可能である。すなわち、樹脂製のピストン本体３８の場合でも実用的な耐久性が得られやすい。ピストン本体３８を樹脂製とすることにより、ピストン組立体１７Ａの軽量化を図ることができる。 In the present embodiment, the damper mechanism 60 is provided to reduce the impact when the stroke end is reached, and the damper mechanism 60 is supported by the piston body 38 so as not to transmit the impact load to the piston body 38 when the stroke end is reached. Therefore, the piston main body 38 only needs to be designed to have a strength that can withstand the pressure from the working fluid, and can be made of resin. That is, even in the case of the resin piston main body 38, practical durability is easily obtained. By making the piston body 38 of resin, the weight of the piston assembly 17A can be reduced.
　本実施形態では、ダンパ機構６０は、ピストンロッド２０の外周部に配置された外周側ダンパ６２を有し、ピストンロッド２０の外周部には、周方向に延在するストッパ装着溝７０が設けられている。ストッパ装着溝７０には、周方向に複数に分割されたストッパ部材７２が装着されている。そして、外周側ダンパ６２はストッパ部材７２を覆っており、これにより、外周側ダンパ６２がストッパ部材７２により支持されるとともにストッパ部材７２がストッパ装着溝７０から離脱することが阻止されている。このような構成の外周側ダンパ６２により、一方のストロークエンド到達時にピストン本体３８に衝撃荷重が伝達されることを良好に阻止することができる。 In the present embodiment, the damper mechanism 60 has an outer periphery side damper 62 disposed on the outer periphery of the piston rod 20, and a stopper mounting groove 70 extending in the circumferential direction is provided on the outer periphery of the piston rod 20. ing. The stopper mounting groove 70 is mounted with a stopper member 72 divided into a plurality in the circumferential direction. The outer circumferential damper 62 covers the stopper member 72, whereby the outer circumferential damper 62 is supported by the stopper member 72 and the stopper member 72 is prevented from being detached from the stopper mounting groove 70. With the outer periphery side damper 62 having such a configuration, it is possible to satisfactorily prevent an impact load from being transmitted to the piston body 38 when one stroke end is reached.
　本実施形態では、ダンパ機構６０は、ピストンロッド２０の端面２０ｃに配置された端部側ダンパ６４を有し、端部側ダンパ６４は、ピストン本体３８とピストンロッド２０との間に保持されるとともに、ピストン本体３８の中心部に設けられた貫通孔３８ａから突出している。このような構成の端部側ダンパ６４により、他方のストロークエンド到達時にピストン本体３８に衝撃荷重が伝達されることを良好に阻止することができる。 In the present embodiment, the damper mechanism 60 has an end-side damper 64 disposed on the end surface 20 c of the piston rod 20, and the end-side damper 64 is held between the piston body 38 and the piston rod 20. At the same time, it protrudes from a through hole 38 a provided at the center of the piston body 38. With the end side damper 64 having such a configuration, it is possible to satisfactorily prevent the impact load from being transmitted to the piston body 38 when the other stroke end is reached.
　本実施形態では、端部側ダンパ６４は、ピストン本体３８とピストンロッド２０との間をシールしている。従って、端部側ダンパ６４が、ピストン本体３８とピストンロッド２０との間のシール部材を兼ねるため、ダンパとシール部材とを別々の部品として設ける構成と比較して、部品点数の削減が図られる。 In the present embodiment, the end side damper 64 seals between the piston main body 38 and the piston rod 20. Therefore, since the end side damper 64 also serves as a seal member between the piston main body 38 and the piston rod 20, the number of parts can be reduced as compared with a configuration in which the damper and the seal member are provided as separate parts. .
　本実施形態では、端部側ダンパ６４は、ピストンロッド２０の端面２０ｃを弾性的に押圧している。この構成により、ピストン本体３８とピストンロッド２０との間のガタツキを防止することができる。 In the present embodiment, the end-side damper 64 elastically presses the end surface 20c of the piston rod 20. With this configuration, rattling between the piston body 38 and the piston rod 20 can be prevented.
　本実施形態では、ピストン本体３８には、ピストン側係合部４０を囲むとともにピストン本体３８の軸方向に深さを有する肉抜き部４６が設けられている。このため、ピストン本体３８を含むピストン組立体１７Ａの軽量化が図られる。そして、ピストン組立体１７Ａの軽量化により、圧力流体の消費量が削減され、省エネルギー化を図ることができる。 In this embodiment, the piston main body 38 is provided with a lightening portion 46 that surrounds the piston-side engaging portion 40 and has a depth in the axial direction of the piston main body 38. For this reason, weight reduction of the piston assembly 17A including the piston main body 38 is achieved. Further, by reducing the weight of the piston assembly 17A, the amount of pressure fluid consumed can be reduced, and energy saving can be achieved.
　本発明は、上述した円形のピストン本体３８に限らず、多角形のピストン本体３８にも適用可能である。従って、流体圧シリンダでは、円形のピストン本体３８を備えたピストン組立体１７Ａに代えて、図５及び図６に示す多角形のピストン本体３８Ａを備えたピストン組立体１７Ｂが採用されてもよい。 The present invention can be applied not only to the above-described circular piston body 38 but also to a polygonal piston body 38. Therefore, in the fluid pressure cylinder, instead of the piston assembly 17A having the circular piston body 38, a piston assembly 17B having the polygonal piston body 38A shown in FIGS. 5 and 6 may be employed.
　ピストン組立体１７Ｂのピストン本体３８Ａは、八角形に構成されている。ピストン本体３８Ａには、周方向に間隔を置いて複数のマグネット装着溝７４が設けられている。具体的に、複数のマグネット装着溝７４は、ピストン本体３８Ａの一方側の面に設けられるとともに、ピストン本体３８Ａの軸方向に深さを有する。１つのマグネット装着溝７４にマグネット７６が装着されている。マグネット７６は、例えば、フェライト磁石、希土類磁石等である。 The piston body 38A of the piston assembly 17B has an octagonal shape. The piston body 38A is provided with a plurality of magnet mounting grooves 74 at intervals in the circumferential direction. Specifically, the plurality of magnet mounting grooves 74 are provided on one surface of the piston main body 38A and have a depth in the axial direction of the piston main body 38A. A magnet 76 is mounted in one magnet mounting groove 74. The magnet 76 is, for example, a ferrite magnet or a rare earth magnet.
[規則91に基づく訂正 29.03.2018]　
　ピストン本体３８Ａの外周部には、環状のパッキン装着溝７８が設けられている。パッキン装着溝７８の底部は周方向に円環状に延在する。パッキン装着溝７８に、弾性部材からなるパッキン７９が装着されている。パッキン７９の外周部形状は、ピストン本体３８Ａと同じ多角形（図６の場合、八角形）に形成されている。パッキン７９の内周部形状は、円形に形成されている。[Correction 29.03.2018 based on Rule 91]
An annular packing mounting groove 78 is provided on the outer peripheral portion of the piston main body 38A. The bottom of the packing mounting groove 78 extends in an annular shape in the circumferential direction. A packing 79 made of an elastic member is mounted in the packing mounting groove 78. The outer peripheral part shape of the packing 79 is formed in the same polygon (an octagon in the case of FIG. 6) as the piston main body 38A. The inner peripheral shape of the packing 79 is circular.
　ピストン組立体１７Ｂの他の部分は、ピストン組立体１７Ａと同様に構成されている。 The other part of the piston assembly 17B is configured in the same manner as the piston assembly 17A.
　ピストン組立体１７Ｂによっても、専用工具や設備や装置を用いることなく手作業で簡単に組立てを行うことができる等、ピストン組立体１７Ａと同様の効果が得られる。 Also with the piston assembly 17B, the same effects as the piston assembly 17A can be obtained, for example, it can be easily assembled manually without using a dedicated tool, equipment or device.
　上述したピストン組立体１７Ａ（図１）では中実構造のピストンロッド２０が採用されているが、図７に示すピストン組立体１７Ｃのように、中空構造のピストンロッド２０Ａが採用されてもよい。この構成により、一層の軽量化及び省エネルギー化が図られたピストン組立体１７Ｃが得られる。なお、ピストンロッド２０Ａの一端側の開口は端部側ダンパ６４により気密又は液密に閉塞されている。 In the above-described piston assembly 17A (FIG. 1), the piston rod 20 having a solid structure is employed, but a piston rod 20A having a hollow structure may be employed as in the piston assembly 17C shown in FIG. With this configuration, it is possible to obtain a piston assembly 17C that is further reduced in weight and energy. Note that the opening on one end side of the piston rod 20 </ b> A is airtightly or liquid tightly closed by the end side damper 64.
　上述したピストン組立体１７Ａ（図１）では、ピストン本体３８の一方側のみに突出するピストンロッド２０が採用されているが、図８Ａ及び図８Ｂに示すピストン組立体１７Ｄ、１７Ｅのように、ピストン本体３８Ｂの両側に突出するピストンロッド８２、８４が採用されてもよい。 In the above-described piston assembly 17A (FIG. 1), the piston rod 20 protruding only on one side of the piston main body 38 is adopted. However, as in the piston assemblies 17D and 17E shown in FIGS. Piston rods 82 and 84 protruding on both sides of the main body 38B may be employed.
　図８Ａに示すピストン組立体１７Ｄは、パッキン装着溝３６及びマグネット装着溝４９が設けられたピストン本体３８Ｂと、ピストン本体３８Ｂに接続されたピストンロッド８２とを有する。ピストン本体３８Ｂは、軸方向の両側にそれぞれピストン側係合部４０（以下、「第１ピストン側係合部４０Ａ」、「第２ピストン側係合部４０Ｂ」という）を有する。 8A has a piston main body 38B provided with a packing mounting groove 36 and a magnet mounting groove 49, and a piston rod 82 connected to the piston main body 38B. The piston main body 38B has piston side engaging portions 40 (hereinafter referred to as “first piston side engaging portion 40A” and “second piston side engaging portion 40B”) on both sides in the axial direction.
　ピストンロッド８２は、第１ピストン側係合部４０Ａに係合する第１ロッド８２Ａと、第２ピストン側係合部４０Ｂに係合する第２ロッド８２Ｂとを有する。第１ロッド８２Ａ及び第２ロッド８２Ｂは、上述したピストンロッド２０と同様に構成されており、中実構造を有する。第１ロッド８２Ａと第２ロッド８２Ｂとの間には、中間部材８３が介装されている。 The piston rod 82 includes a first rod 82A that engages with the first piston-side engaging portion 40A and a second rod 82B that engages with the second piston-side engaging portion 40B. The first rod 82A and the second rod 82B are configured similarly to the piston rod 20 described above, and have a solid structure. An intermediate member 83 is interposed between the first rod 82A and the second rod 82B.
　中間部材８３は、上述した外周側ダンパ６２と同様の弾性材料により構成されるとよい。これにより、中間部材８３が第１ロッド８２Ａの端面８２Ａ１及び第２ロッド８２Ｂの端面８２Ｂ１を押圧し、ピストン本体３８Ｂと第１ロッド８２Ａとの間のガタツキが抑制されるとともに、ピストン本体３８Ｂと第２ロッド８２Ｂとの間のガタツキが抑制される。中間部材８３は、ピストン本体３８Ｂ、第１ロッド８２Ａ及び第２ロッド８２Ｂと密着しており、これにより、第１ロッド８２Ａ側と第２ロッド８２Ｂ側のエアシールを兼ねている。 The intermediate member 83 may be made of an elastic material similar to that of the outer peripheral side damper 62 described above. Thereby, the intermediate member 83 presses the end surface 82A1 of the first rod 82A and the end surface 82B1 of the second rod 82B, and rattling between the piston main body 38B and the first rod 82A is suppressed, and the piston main body 38B and the first The backlash between the two rods 82B is suppressed. The intermediate member 83 is in close contact with the piston main body 38B, the first rod 82A, and the second rod 82B, thereby also serving as an air seal for the first rod 82A side and the second rod 82B side.
　ピストンロッド２０（図１）と同様に、第１ロッド８２Ａ及び第２ロッド８２Ｂの外周部にはそれぞれ外周側ダンパ６２が配置されるとともに、第１ロッド８２Ａ及び第２ロッド８２Ｂに装着されたストッパ部材７２により外周側ダンパ６２がそれぞれ支持されている。 As with the piston rod 20 (FIG. 1), outer peripheral side dampers 62 are disposed on the outer peripheral portions of the first rod 82A and the second rod 82B, respectively, and stoppers mounted on the first rod 82A and the second rod 82B. The outer periphery side dampers 62 are supported by the members 72, respectively.
　図８Ｂに示すピストン組立体１７Ｅは、図８Ａに示したピストン組立体１７Ｄにおける第１ロッド８２Ａ、第２ロッド８２Ｂ及び中間部材８３を中空構造に変更したものである。すなわち、ピストン組立体１７Ｅは、ピストン本体３８Ｂと、ピストン本体３８Ｂに接続された中空状のピストンロッド８４（第１ロッド８４Ａ及び第２ロッド８４Ｂ）とを有し、第１ロッド８４Ａと第２ロッド８４Ｂとの間には中空状の中間部材８３ａが介装されている。 A piston assembly 17E shown in FIG. 8B is obtained by changing the first rod 82A, the second rod 82B, and the intermediate member 83 in the piston assembly 17D shown in FIG. 8A to a hollow structure. That is, the piston assembly 17E includes a piston main body 38B and hollow piston rods 84 (first rod 84A and second rod 84B) connected to the piston main body 38B, and the first rod 84A and the second rod. A hollow intermediate member 83a is interposed between 84B and 84B.
　ピストン組立体１７Ａ（図１）では、外周側ダンパ６２と端部側ダンパ６４の両方が設けられているが、図９Ａに示すピストン組立体１７Ｆのように、ダンパ機構としては外周側ダンパ６２のみが設けられてもよい。ピストン組立体１７Ｆのピストン本体３８Ｃは、軸方向に貫通した貫通孔が設けられていないこと以外は、ピストン組立体１７Ａのピストン本体３８と同様に構成されている。あるいは、ダンパ機構としては端部側ダンパ６４のみが設けられてもよい（ピストン組立体１７Ａにおいて外周側ダンパ６２が省略されてもよい）。図９Ｂに示すピストン組立体１７Ｇのように、ダンパ機構が設けられていなくてもよい。 In the piston assembly 17A (FIG. 1), both the outer peripheral side damper 62 and the end side damper 64 are provided. However, like the piston assembly 17F shown in FIG. 9A, only the outer peripheral side damper 62 is used as a damper mechanism. May be provided. The piston body 38C of the piston assembly 17F is configured in the same manner as the piston body 38 of the piston assembly 17A, except that a through hole penetrating in the axial direction is not provided. Alternatively, only the end side damper 64 may be provided as the damper mechanism (the outer peripheral side damper 62 may be omitted in the piston assembly 17A). Like the piston assembly 17G shown in FIG. 9B, the damper mechanism may not be provided.
　ピストン組立体１７Ａ（図１）において、マグネット４８は省略されてもよい。この場合、図１０Ａに示すピストン組立体１７Ｈのように、ピストン本体３８にマグネット装着溝４９を残したままとしてもよい。あるいは、図１０Ｂに示すピストン組立体１７Ｉのように、マグネット装着溝を省略したピストン本体３８Ｄが採用されてもよい。 In the piston assembly 17A (FIG. 1), the magnet 48 may be omitted. In this case, the magnet mounting groove 49 may be left in the piston main body 38 as in the piston assembly 17H shown in FIG. 10A. Or the piston main body 38D which abbreviate | omitted the magnet installation groove | channel like the piston assembly 17I shown to FIG. 10B may be employ | adopted.
　ピストン組立体１７Ａ（図１）では、ピストン本体３８が低摩擦材からなる場合、ピストン外周部３８ｂがウエアリングとして機能する。これと異なり、図１１に示すピストン組立体１７Ｊのように、環状のウエアリング装着溝８６が設けられたピストン本体３８Ｅが採用され、ウエアリング装着溝８６に低摩擦材からなるウエアリング８８が装着されてもよい。 In the piston assembly 17A (FIG. 1), when the piston main body 38 is made of a low friction material, the piston outer peripheral portion 38b functions as a wear ring. Unlike the piston assembly 17J shown in FIG. 11, a piston body 38E provided with an annular wear ring mounting groove 86 is employed, and a wear ring 88 made of a low friction material is mounted in the wear ring mounting groove 86. May be.
　ウエアリング８８は、ピストン本体３８Ｅの外周面が摺動孔１３（図１）の内周面に接触することを防止するための環状部材である。ウエアリング８８の外径は、ピストン本体３８Ｅの外形よりも大きい。低摩擦材としては、例えば、四フッ化エチレン（ＰＴＦＥ）のような低摩擦性と耐摩耗性とを兼ね備えた合成樹脂材料や、金属材料（例えば、軸受鋼）等が挙げられる。 Wear ring 88 is an annular member for preventing the outer peripheral surface of piston body 38E from contacting the inner peripheral surface of sliding hole 13 (FIG. 1). The outer diameter of the wear ring 88 is larger than the outer shape of the piston main body 38E. Examples of the low friction material include a synthetic resin material having both low friction and wear resistance such as tetrafluoroethylene (PTFE), a metal material (for example, bearing steel), and the like.
　図１２に示すピストン組立体１７Ｋのように、マグネット及びウエアリングが装着されないピストン本体３８Ｆが採用されるとともに、ダンパ機構が省略されてもよい。 As with the piston assembly 17K shown in FIG. 12, a piston main body 38F to which no magnet and wear ring are attached is adopted, and the damper mechanism may be omitted.
　図１３に示す流体圧シリンダ１０Ｂは、中空筒状のシリンダチューブ１０２（ボディ）と、シリンダチューブ１０２の一端部に配置されたヘッドカバー１０４と、シリンダチューブ１０２の他端部に配置されたロッドカバー１０６とを備える。流体圧シリンダ１０Ｂは、さらに、シリンダチューブ１０２に対して往復移動可能に配置されたピストン組立体１７Ｌと、ダンパ機構６０Ａと、ピストンユニット１８の一方及び他方のストロークエンドにおける衝撃を緩和するクッション機構１１０とを備える。ピストン組立体１７Ｌは、シリンダチューブ１０２内に軸方向（矢印Ｘ方向）に移動可能に配置されたピストンユニット１８と、ピストンユニット１８に連結されたピストンロッド１０８とを有する。 A fluid pressure cylinder 10B shown in FIG. 13 includes a hollow cylindrical cylinder tube 102 (body), a head cover 104 disposed at one end of the cylinder tube 102, and a rod cover 106 disposed at the other end of the cylinder tube 102. With. The fluid pressure cylinder 10B further includes a piston assembly 17L disposed so as to be reciprocally movable with respect to the cylinder tube 102, a damper mechanism 60A, and a cushion mechanism 110 that alleviates an impact at one and the other stroke ends of the piston unit 18. With. The piston assembly 17L includes a piston unit 18 disposed in the cylinder tube 102 so as to be movable in the axial direction (arrow X direction), and a piston rod 108 coupled to the piston unit 18.
　シリンダチューブ１０２は、円筒体からなり、その内部にはピストンユニット１８が収容されヘッドカバー１０４及びロッドカバー１０６によって閉塞された摺動孔１０３（シリンダ室）が形成されている。 The cylinder tube 102 is formed of a cylindrical body, and a sliding hole 103 (cylinder chamber) in which the piston unit 18 is accommodated and closed by the head cover 104 and the rod cover 106 is formed.
　ヘッドカバー１０４の第１段付き部１１２が、シリンダチューブ１０２の矢印Ｘ２方向側の端部に挿入されている。ヘッドカバー１０４には、第１中央空洞部１１６と、この第１中央空洞部１１６と連通した第１ポート１１８が形成されている。第１ポート１１８を介して、圧力流体の供給・排出が行われる。 The first stepped portion 112 of the head cover 104 is inserted into the end of the cylinder tube 102 on the arrow X2 direction side. The head cover 104 is formed with a first central cavity 116 and a first port 118 communicating with the first central cavity 116. Pressure fluid is supplied and discharged through the first port 118.
　ロッドカバー１０６の第２段付き部１２０が、シリンダチューブ１０２の矢印Ｘ１方向側の端部に挿入されている。ロッドカバー１０６には、第２中央空洞部１２４と、この第２中央空洞部１２４と連通した第２ポート１２６が形成されている。第２ポート１２６を介して、圧力流体の供給・排出が行われる。ロッドカバー１０６の内周部にはリング状のブッシュ１３０及びパッキン１３２が配置されている。 The second stepped portion 120 of the rod cover 106 is inserted into the end of the cylinder tube 102 on the arrow X1 direction side. The rod cover 106 is formed with a second central cavity portion 124 and a second port 126 communicating with the second central cavity portion 124. Pressure fluid is supplied and discharged through the second port 126. A ring-shaped bush 130 and packing 132 are disposed on the inner peripheral portion of the rod cover 106.
　ピストンユニット１８は、ピストン組立体１７Ａ（図１）のピストンユニット１８と同様に構成されている。 The piston unit 18 is configured similarly to the piston unit 18 of the piston assembly 17A (FIG. 1).
　ダンパ機構６０Ａは、ピストンロッド１０８の外周部に配置された外周側ダンパ６２（図１に示す外周側ダンパ６２と同一構成）と、ピストンロッド１０８の端面１０８ａに配置された端部側ダンパ６４Ａとを有する。外周側ダンパ６２は、第２クッション部材１４２のピストン本体３８側の端部に位置している。端部側ダンパ６４Ａは、端部側ダンパ６４（図１）を中空状に改変したものであり、ピストンロッド１０８の端面１０８ａとピストン本体３８の内周部との間に保持されている。 The damper mechanism 60A includes an outer peripheral damper 62 (same configuration as the outer peripheral damper 62 shown in FIG. 1) disposed on the outer periphery of the piston rod 108, an end damper 64A disposed on the end surface 108a of the piston rod 108, Have The outer peripheral damper 62 is located at the end of the second cushion member 142 on the piston main body 38 side. The end side damper 64 </ b> A is obtained by modifying the end side damper 64 (FIG. 1) into a hollow shape, and is held between the end surface 108 a of the piston rod 108 and the inner peripheral portion of the piston main body 38.
　クッション機構１１０は、可動部（ピストンロッド１０８）側に設けられた第１クッション部材１４０及び第２クッション部材１４２（クッションリング）と、固定部（ヘッドカバー１０４及びロッドカバー１０６）側に設けられた弾性部材からなるリング状の第１クッションシール１４４及び第２クッションシール１４６とを有する。 The cushion mechanism 110 includes a first cushion member 140 and a second cushion member 142 (cushion ring) provided on the movable portion (piston rod 108) side, and an elasticity provided on the fixed portion (head cover 104 and rod cover 106) side. It has the ring-shaped 1st cushion seal 144 and 2nd cushion seal 146 which consist of members.
　第１クッション部材１４０は、ピストンロッド１０８の矢印Ｘ２方向側の端部においてピストンロッド１０８と同軸状に設けられている。具体的に、第１クッション部材１４０は、ピストンロッド１０８よりも小径に形成されるとともに、ピストンロッド１０８の端面１０８ａ及び端部側ダンパ６４Ａの端面から矢印Ｘ２方向に突出している。第１クッション部材１４０は、中空又は中実の円筒状に形成されている。第１クッション部材１４０の外径は、端部側ダンパ６４Ａの外径よりも小さい。 The first cushion member 140 is provided coaxially with the piston rod 108 at the end of the piston rod 108 on the arrow X2 direction side. Specifically, the first cushion member 140 is formed with a smaller diameter than the piston rod 108, and protrudes in the direction of the arrow X2 from the end surface 108a of the piston rod 108 and the end surface of the end-side damper 64A. The first cushion member 140 is formed in a hollow or solid cylindrical shape. The outer diameter of the first cushion member 140 is smaller than the outer diameter of the end side damper 64A.
　第１クッション部材１４０は、ピストンロッド１０８と一体成形された部分であってもよく、あるいは、ピストンロッド１０８と接合された別部品であってもよい。第１クッション部材１４０がピストンロッド１０８と別部品の場合、第１クッション部材１４０は、例えば、溶接、接着、螺合等の接合手段によって、ピストンロッド１０８と接合され得る。 The first cushion member 140 may be a part formed integrally with the piston rod 108 or may be a separate part joined to the piston rod 108. When the first cushion member 140 is a separate component from the piston rod 108, the first cushion member 140 can be joined to the piston rod 108 by joining means such as welding, adhesion, and screwing.
　第１クッションシール１４４は、リング状の第１ホルダ１４８の内周部に保持されている。第１ホルダ１４８は、ヘッドカバー１０４の第１段付き部１１２の内周部に固定されている。第１ホルダ１４８の孔部１４８ａに第１クッション部材１４０が挿入されていない状態では、摺動孔１０３と第１中央空洞部１１６は、孔部１４８ａを介して連通している。第１ホルダ１４８の孔部１４８ａに第１クッション部材１４０が挿入される際に、第１クッションシール１４４は、全周に亘って第１クッション部材１４０の外周面に摺接する。 The first cushion seal 144 is held on the inner periphery of the ring-shaped first holder 148. The first holder 148 is fixed to the inner peripheral portion of the first stepped portion 112 of the head cover 104. When the first cushion member 140 is not inserted into the hole 148a of the first holder 148, the sliding hole 103 and the first central cavity 116 communicate with each other via the hole 148a. When the first cushion member 140 is inserted into the hole 148a of the first holder 148, the first cushion seal 144 is in sliding contact with the outer peripheral surface of the first cushion member 140 over the entire circumference.
　第２クッション部材１４２は、ピストンユニット１８のロッドカバー１０６側（矢印Ｘ１方向側）に隣接して、ピストンユニット１８の近傍において、ピストンロッド１０８と同軸状に設けられている。第２クッション部材１４２は、ピストンロッド１０８よりも大径且つピストンユニット１８よりも小径に形成されたリング状の部材であり、ピストンロッド１０８の外周面に、例えば、溶接、接着等により接合されている。図１３において、第２クッション部材１４２の外径は、ピストンロッド１０８の外径よりも若干大きい程度である。 The second cushion member 142 is adjacent to the rod cover 106 side (arrow X1 direction side) of the piston unit 18 and is provided coaxially with the piston rod 108 in the vicinity of the piston unit 18. The second cushion member 142 is a ring-shaped member having a larger diameter than the piston rod 108 and a smaller diameter than the piston unit 18, and is joined to the outer peripheral surface of the piston rod 108 by, for example, welding or adhesion. Yes. In FIG. 13, the outer diameter of the second cushion member 142 is slightly larger than the outer diameter of the piston rod 108.
　第２クッションシール１４６は、リング状の第２ホルダ１５０の内周部に保持されている。第２ホルダ１５０は、ロッドカバー１０６の第２段付き部１２０の内周部に固定されている。第２ホルダ１５０の孔部１５０ａに第２クッション部材１４２が挿入されていない状態では、摺動孔１０３と第２中央空洞部１２４は、孔部１５０ａを介して連通している。第２ホルダ１５０の孔部１５０ａに第２クッション部材１４２が挿入される際に、第２クッションシール１４６は、全周に亘って第２クッション部材１４２の外周面に摺接する。 The second cushion seal 146 is held on the inner periphery of the ring-shaped second holder 150. The second holder 150 is fixed to the inner peripheral portion of the second stepped portion 120 of the rod cover 106. When the second cushion member 142 is not inserted into the hole 150a of the second holder 150, the sliding hole 103 and the second central cavity 124 communicate with each other through the hole 150a. When the second cushion member 142 is inserted into the hole 150a of the second holder 150, the second cushion seal 146 is in sliding contact with the outer peripheral surface of the second cushion member 142 over the entire circumference.
　次に、上記のように構成された流体圧シリンダ１０Ｂの作用を説明する。なお、以下の説明では、圧力流体としてエア（圧縮エア）を用いる場合を説明するが、エア以外の気体を用いてもよい。 Next, the operation of the fluid pressure cylinder 10B configured as described above will be described. In the following description, a case where air (compressed air) is used as the pressure fluid will be described, but a gas other than air may be used.
　流体圧シリンダ１０Ｂは、第１ポート１１８又は第２ポート１２６を介して導入される圧力流体の作用によって、ピストンユニット１８を摺動孔１０３内で軸方向に移動させる。これにより、当該ピストンユニット１８に連結されたピストンロッド１０８が進退移動する。 The fluid pressure cylinder 10 </ b> B moves the piston unit 18 in the axial direction in the sliding hole 103 by the action of the pressure fluid introduced through the first port 118 or the second port 126. Thereby, the piston rod 108 connected to the piston unit 18 moves forward and backward.
　具体的に、ピストンユニット１８が図１３に示す後退位置に位置している状態で、第２ポート１２６を大気開放状態とし、図示しない圧力流体供給源から第１ポート１１８及び第１中央空洞部１１６及び孔部１４８ａを介して、エアを第１圧力室１０３ａへと供給する。これにより、ピストンユニット１８がピストンロッド１０８とともにロッドカバー１０６側へと変位（前進）する。この場合、第２圧力室１０３ｂ内のエアは、第２ホルダ１５０の孔部１５０ａ及び第２中央空洞部１２４を介して、第２ポート１２６から排出される。 Specifically, in a state where the piston unit 18 is located at the retracted position shown in FIG. 13, the second port 126 is opened to the atmosphere, and the first port 118 and the first central cavity 116 116 from a pressure fluid supply source (not shown). In addition, air is supplied to the first pressure chamber 103a through the hole 148a. As a result, the piston unit 18 is displaced (advanced) together with the piston rod 108 toward the rod cover 106 side. In this case, the air in the second pressure chamber 103 b is discharged from the second port 126 through the hole 150 a of the second holder 150 and the second central cavity 124.
　そして、外周側ダンパ６２が第２ホルダ１５０に当接することで、ピストンユニット１８の前進動作が停止する。なお、外周側ダンパ６２は、ピストンユニット１８が前進位置に来た際にロッドカバー１０６（及び第２ホルダ１５０）に当接する大きさに形成されてもよい。 Then, the forward movement of the piston unit 18 is stopped by the outer peripheral damper 62 coming into contact with the second holder 150. In addition, the outer periphery side damper 62 may be formed in the magnitude | size which contact | abuts to the rod cover 106 (and 2nd holder 150), when the piston unit 18 comes to an advance position.
　ピストンユニット１８が前進位置へと近づく際、第２クッション部材１４２は第２ホルダ１５０の孔部１５０ａに挿入される。これに伴い、第２クッションシール１４６の内周部が第２クッション部材１４２の外周面に接触して、この接触部分に気密シールが形成される。 When the piston unit 18 approaches the forward position, the second cushion member 142 is inserted into the hole 150a of the second holder 150. Accordingly, the inner peripheral portion of the second cushion seal 146 contacts the outer peripheral surface of the second cushion member 142, and an airtight seal is formed at this contact portion.
　この結果、第２圧力室１０３ｂにエアクッションが形成される。第２圧力室１０３ｂのエアクッションは、ピストンユニット１８がロッドカバー１０６側に変位する際の変位抵抗となることで、ロッドカバー１０６側のストロークエンド付近でピストンユニット１８の変位を減速させる。従って、ピストンユニット１８がストロークエンドに到達した際の衝撃が一層緩和される。なお、エアは、図示しない小さな孔部を介して第２ポート１２６へ少量ずつ排気される。 As a result, an air cushion is formed in the second pressure chamber 103b. The air cushion in the second pressure chamber 103b serves as a displacement resistance when the piston unit 18 is displaced toward the rod cover 106, thereby decelerating the displacement of the piston unit 18 near the stroke end on the rod cover 106 side. Therefore, the impact when the piston unit 18 reaches the stroke end is further alleviated. The air is exhausted little by little to the second port 126 through a small hole (not shown).
　一方、ピストンユニット１８が前進位置（ロッドカバー１０６側のストロークエンド）に位置している状態で、第１ポート１１８を大気開放状態とし、図示しない圧力流体供給源から第２ポート１２６、第２中央空洞部１２４及び孔部１５０ａを介して、エアを第２圧力室１０３ｂへと供給する。これにより、ピストンユニット１８がヘッドカバー１０４側へと変位（後退）する。この場合、第１圧力室１０３ａ内のエアは、第１ホルダ１４８の孔部１４８ａ及び第１中央空洞部１１６を介して、第１ポート１１８から排出される。そして、端部側ダンパ６４Ａが第１ホルダ１４８に当接することで、ピストンユニット１８の後退動作が停止する。 On the other hand, in a state where the piston unit 18 is located at the forward position (stroke end on the rod cover 106 side), the first port 118 is opened to the atmosphere, and the second port 126 and the second center are connected from a pressure fluid supply source (not shown). Air is supplied to the second pressure chamber 103b through the cavity 124 and the hole 150a. As a result, the piston unit 18 is displaced (retracted) toward the head cover 104 side. In this case, the air in the first pressure chamber 103 a is discharged from the first port 118 through the hole 148 a of the first holder 148 and the first central cavity 116. Then, when the end side damper 64A comes into contact with the first holder 148, the backward movement of the piston unit 18 is stopped.
　ピストンユニット１８が後退位置へと近づく際、第１クッション部材１４０は第１ホルダ１４８の孔部１４８ａに挿入される。これに伴い、第１クッションシール１４４の内周部が第１クッション部材１４０の外周面に接触して、この接触部分に気密シールが形成される。 When the piston unit 18 approaches the retracted position, the first cushion member 140 is inserted into the hole 148a of the first holder 148. Accordingly, the inner peripheral portion of the first cushion seal 144 comes into contact with the outer peripheral surface of the first cushion member 140, and an airtight seal is formed at this contact portion.
　この結果、第１圧力室１０３ａにエアクッションが形成される。第１圧力室１０３ａのエアクッションは、ピストンユニット１８がヘッドカバー１０４側に変位する際の変位抵抗となることで、ヘッドカバー１０４側のストロークエンド付近でピストンユニット１８の変位を減速させる。従って、ピストンユニット１８がストロークエンドに到達した際の衝撃が一層緩和される。 As a result, an air cushion is formed in the first pressure chamber 103a. The air cushion in the first pressure chamber 103a serves as a displacement resistance when the piston unit 18 is displaced toward the head cover 104, thereby decelerating the displacement of the piston unit 18 near the stroke end on the head cover 104 side. Therefore, the impact when the piston unit 18 reaches the stroke end is further alleviated.
　図１４Ａに示す流体圧シリンダ１０Ｃは、いわゆる単動型シリンダとして構成されている。具体的に、この流体圧シリンダ１０Ｃは、流体圧シリンダ１０Ａ（図１）において、ピストンユニット１８とロッドカバー１６との間にスプリング１５４を配置したものである。この場合、第２ポート１２ｂは大気開放されている。 The fluid pressure cylinder 10C shown in FIG. 14A is configured as a so-called single acting cylinder. Specifically, the fluid pressure cylinder 10 </ b> C is obtained by arranging a spring 154 between the piston unit 18 and the rod cover 16 in the fluid pressure cylinder 10 </ b> A (FIG. 1). In this case, the second port 12b is open to the atmosphere.
　流体圧シリンダ１０Ｃにおいて、第１ポート１２ａを介して第１圧力室１３ａに圧力流体を供給すると、圧力流体によってピストンユニット１８がロッドカバー１６側へと変位（前進）し、前進位置のストロークエンドへと到達する。そして、第１ポート１２ａへの圧力流体の供給を停止するとともに、第１ポート１２ａを大気開放すると、ピストンユニット１８はスプリング１５４の弾性付勢力によってヘッドカバー１４側へと変位（後退）し、後退位置のストロークエンドへと到達する。 In the fluid pressure cylinder 10C, when pressure fluid is supplied to the first pressure chamber 13a via the first port 12a, the piston unit 18 is displaced (advanced) toward the rod cover 16 by the pressure fluid, and the stroke end of the advance position is reached. And reach. When the supply of pressurized fluid to the first port 12a is stopped and the first port 12a is opened to the atmosphere, the piston unit 18 is displaced (retracted) toward the head cover 14 by the elastic biasing force of the spring 154, and the retracted position. To reach the stroke end.
　図１４Ｂに示す流体圧シリンダ１０Ｄも、いわゆる単動型シリンダとして構成されている。具体的に、この流体圧シリンダ１０Ｄは、流体圧シリンダ１０Ａ（図１）において、ピストンユニット１８とヘッドカバー１４との間にスプリング１５４を配置したものである。この場合、第１ポート１２ａは大気開放されている。 The fluid pressure cylinder 10D shown in FIG. 14B is also configured as a so-called single acting cylinder. Specifically, the fluid pressure cylinder 10 </ b> D is obtained by arranging a spring 154 between the piston unit 18 and the head cover 14 in the fluid pressure cylinder 10 </ b> A (FIG. 1). In this case, the first port 12a is open to the atmosphere.
　流体圧シリンダ１０Ｄにおいて、第２ポート１２ｂを介して第２圧力室１３ｂに圧力流体を供給すると、圧力流体によってピストンユニット１８がヘッドカバー１４側へと変位（後退）し、後退位置のストロークエンドへと到達する。そして、第２ポート１２ｂへの圧力流体の供給を停止するとともに、第２ポート１２ｂを大気開放すると、ピストンユニット１８はスプリング１５４の弾性付勢力によってロッドカバー１６側へと変位（前進）し、前進位置のストロークエンドへと到達する。 In the fluid pressure cylinder 10D, when the pressure fluid is supplied to the second pressure chamber 13b via the second port 12b, the piston unit 18 is displaced (retracted) toward the head cover 14 by the pressure fluid, and the stroke end of the retracted position is reached. To reach. When the supply of the pressure fluid to the second port 12b is stopped and the second port 12b is opened to the atmosphere, the piston unit 18 is displaced (advanced) to the rod cover 16 side by the elastic biasing force of the spring 154, and advances. The stroke end of the position is reached.
　上述した流体圧シリンダ１０Ａ～１０Ｄでは、図１５及び図１６に示すピストン組立体１７Ｍが採用されてもよい。ピストン組立体１７Ｍは、ピストンユニット１８ａと、ピストンユニット１８ａに連結されたピストンロッド１６０とを有する。 In the fluid pressure cylinders 10A to 10D described above, a piston assembly 17M shown in FIGS. 15 and 16 may be employed. The piston assembly 17M includes a piston unit 18a and a piston rod 160 connected to the piston unit 18a.
　ピストンユニット１８ａは、ピストンロッド１６０に接続されたピストン本体１６２と、ピストン本体１６２の外周部に装着されたパッキン３４及びマグネット４８とを有する。ピストン本体１６２の構成材料は、上述したピストン本体３８（図１等）の構成材料として例示した材料から選択し得る。ピストン本体１６２とピストンロッド１６０との間には端部側ダンパ６４が配置されている。端部側ダンパ６４は、ピストン本体１６２に設けられた貫通孔１６２ａに装着されている。 The piston unit 18 a includes a piston main body 162 connected to the piston rod 160, and a packing 34 and a magnet 48 attached to the outer periphery of the piston main body 162. The constituent material of the piston main body 162 can be selected from the materials exemplified as the constituent material of the piston main body 38 (FIG. 1 and the like) described above. An end side damper 64 is disposed between the piston main body 162 and the piston rod 160. The end side damper 64 is attached to a through hole 162 a provided in the piston main body 162.
　ピストン本体１６２には、ピストン側係合部１６６が一体成形により設けられている。ピストン側係合部１６６は、側方に開口した形状を有する。図１６において、ピストン側係合部１６６は、ピストン本体１６２の端面１６２ｂから軸方向（矢印Ｘ方向）に膨出するとともに軸方向から見てＵ字状に構成されている。ピストン側係合部１６６の内周面に、Ｕ字状係合溝１６６ａが設けられている。 The piston main body 162 is provided with a piston-side engaging portion 166 by integral molding. The piston side engaging portion 166 has a shape opened to the side. In FIG. 16, the piston-side engaging portion 166 bulges in the axial direction (arrow X direction) from the end surface 162 b of the piston main body 162 and is configured in a U shape when viewed from the axial direction. A U-shaped engagement groove 166 a is provided on the inner peripheral surface of the piston-side engagement portion 166.
　ピストン側係合部１６６は、貫通孔１６２ａの外周形状に沿って円弧状に延在した湾曲部１６７と、湾曲部１６７の両端からそれぞれ直線状に且つ互いに平行に延出した２つのアーム部１６８とを有する。ピストン本体１６２の軸方向から見て、２つのアーム部１６８の先端は、貫通孔１６２ａよりも径方向外側に位置する。 The piston-side engaging portion 166 includes a curved portion 167 extending in an arc shape along the outer peripheral shape of the through hole 162a, and two arm portions 168 extending linearly and parallel to each other from both ends of the curved portion 167. And have. When viewed from the axial direction of the piston main body 162, the distal ends of the two arm portions 168 are located radially outside of the through hole 162a.
　このように、ピストン本体１６２には、Ｕ字状に構成されたピストン側係合部１６６が設けられている。このため、ピストン側係合部１６６が補強リブとして機能し、ピストン本体１６２が補強される。これにより、ピストン組立体１７Ｍが組み込まれた流体圧シリンダの作動時に発生する静圧に対するピストン本体１６２の強度を向上させることができる。 Thus, the piston main body 162 is provided with the piston-side engaging portion 166 configured in a U-shape. For this reason, the piston side engaging part 166 functions as a reinforcing rib, and the piston main body 162 is reinforced. Thereby, the intensity | strength of the piston main body 162 with respect to the static pressure generate | occur | produced at the time of the action | operation of the fluid pressure cylinder in which the piston assembly 17M was integrated can be improved.
　ピストンロッド１６０の基端部１６０ａには、ピストン側係合部１６６のＵ字状係合溝１６６ａに係合したロッド側係合部４２が設けられている。ロッド側係合部４２は、環状の係合突起５６により構成されている。係合突起５６に隣接して環状溝５８が形成されている。係合突起５６がＵ字状のピストン側係合部１６６に側方から挿入されることにより、ピストン本体１６２とピストンロッド１６０との軸方向の相対変位が規制されている。ピストンロッド１６０の構成材料は、上述したピストンロッド２０（図１等）の構成材料として例示した材料から選択し得る。 At the base end portion 160a of the piston rod 160, a rod side engaging portion 42 engaged with the U-shaped engaging groove 166a of the piston side engaging portion 166 is provided. The rod side engaging portion 42 is configured by an annular engaging protrusion 56. An annular groove 58 is formed adjacent to the engagement protrusion 56. When the engagement protrusion 56 is inserted into the U-shaped piston side engagement portion 166 from the side, the relative displacement in the axial direction between the piston main body 162 and the piston rod 160 is restricted. The constituent material of the piston rod 160 can be selected from the materials exemplified as the constituent material of the piston rod 20 (FIG. 1 and the like) described above.
　ピストンロッド１６０の外周部には、矢印Ｘ１方向側のストロークエンド到達時の衝撃を緩和する弾性材料からなるリング状の外周側ダンパ１７０が配置されている。ピストン本体１６２と外周側ダンパ１７０との間には、リング状のスペーサ１７２が介装されている。スペーサ１７２はピストン側係合部１６６と当接している。 On the outer peripheral portion of the piston rod 160, a ring-shaped outer peripheral damper 170 made of an elastic material that relieves an impact when reaching the stroke end in the direction of the arrow X1 is disposed. A ring-shaped spacer 172 is interposed between the piston main body 162 and the outer peripheral side damper 170. The spacer 172 is in contact with the piston side engaging portion 166.
　ピストン本体１６２、スペーサ１７２及び外周側ダンパ１７０は軸方向に積層されている。スペーサ１７２は、外周側ダンパ１７０よりも硬質な材料により構成されている。スペーサ１７２の構成材料は、上述したピストンロッド２０（図１等）の構成材料として挙げた材料から選択され得る。 The piston main body 162, the spacer 172, and the outer peripheral side damper 170 are laminated in the axial direction. The spacer 172 is made of a material harder than the outer peripheral damper 170. The constituent material of the spacer 172 may be selected from the materials listed as the constituent material of the piston rod 20 (FIG. 1 and the like) described above.
　ピストン組立体１７Ｍの構造では、矢印Ｘ１方向側のストロークエンド到達時の荷重は外周側ダンパ１７０を介してピストン本体１６２に伝わる。従って、ピストン本体１６２がストロークエンド到達時の荷重を受ける。ピストン本体１６２が金属材料により構成される場合、樹脂材料よりも強度が高いため、ピストン本体１６２の強度を十分に確保することができる。 In the structure of the piston assembly 17M, the load when reaching the stroke end in the direction of the arrow X1 is transmitted to the piston main body 162 via the outer peripheral damper 170. Accordingly, the piston body 162 receives a load when the stroke end is reached. When the piston main body 162 is made of a metal material, the strength of the piston main body 162 can be sufficiently secured because the strength is higher than that of the resin material.
　その際、ピストン本体１６２と外周側ダンパ１７０との間には、外周側ダンパ１７０よりも硬質なリング状のスペーサ１７２が介装されているため、外周側ダンパ１７０は、Ｕ字状のピストン側係合部１６６ではなくリング状のスペーサ１７２により、全周に亘って支持される。従って、弾性材料により構成される外周側ダンパ１７０がストロークエンド到達時の荷重で破損することを防止することができる。 At that time, a ring-shaped spacer 172 that is harder than the outer peripheral damper 170 is interposed between the piston main body 162 and the outer peripheral damper 170, so that the outer peripheral damper 170 has a U-shaped piston side. The entire periphery is supported not by the engaging portion 166 but by the ring-shaped spacer 172. Therefore, it is possible to prevent the outer peripheral damper 170 made of an elastic material from being damaged by a load when reaching the stroke end.
　本発明は上述した実施形態に限定されるものではなく、本発明の要旨を逸脱しない範囲において、種々の改変が可能である。例えば、本発明は、ピストンユニット及びシリンダチューブの断面形状が非円形（四角形状や、楕円形状等の長円形状等）の流体圧シリンダにも適用可能である（図５のピストン組立体１７Ｂはその一例である）。また、本発明は、複数のピストン及びピストンロッドを備えた多ロッド型（デュアルロッド型等）の流体圧シリンダにも適用可能である。 The present invention is not limited to the above-described embodiment, and various modifications can be made without departing from the gist of the present invention. For example, the present invention can also be applied to a hydraulic cylinder whose piston unit and cylinder tube have non-circular cross-sectional shapes (such as a square shape or an elliptical shape such as an elliptical shape) (the piston assembly 17B in FIG. One example). The present invention can also be applied to a multi-rod type (dual rod type or the like) fluid pressure cylinder having a plurality of pistons and piston rods.
　また、本発明は、アクチュエータ等として用いられる流体圧シリンダに限らず、ピストンを有する他の形態の流体圧装置にも適用可能である。本発明を適用できるピストンを有する他の形態の流体圧装置としては、例えば、ピストンによって弁体を移動させて流路の切り換えをするバルブ装置、ピストンロッドを入力軸としてこれに連結されたピストンを変位させて測長を行う測長シリンダ、ピストンを変位させることによりピストンロッドを介してピストンと連結されたテーブルを変位させるスライドテーブル、ピストンを変位させこのピストン変位を変換することで開閉動作する把持部によってワークを把持するチャック装置、等が挙げられる。 The present invention is not limited to a fluid pressure cylinder used as an actuator or the like, but can be applied to other forms of fluid pressure devices having a piston. Other forms of fluid pressure devices having a piston to which the present invention can be applied include, for example, a valve device that switches a flow path by moving a valve body by a piston, and a piston that is connected to the piston rod as an input shaft. A measuring cylinder that measures the length by displacing it, a slide table that displaces the table that is connected to the piston via the piston rod by displacing the piston, and a grip that opens and closes by displacing the piston and converting this piston displacement And a chuck device for gripping a workpiece by the portion.

Claims (15)

  1. 　摺動孔（１３、１０３）内を軸方向に変位可能なピストン本体（３８、３８Ａ～３８Ｆ、１６２）と、前記ピストン本体（３８、３８Ａ～３８Ｆ、１６２）から軸方向に突出したピストンロッド（２０、２０Ａ、８２、８４、１０８、１６０）とを備えたピストン組立体（１７Ａ～１７Ｍ）であって、
    　前記ピストン本体（３８、３８Ａ～３８Ｆ、１６２）は、ピストン側係合部（４０、１６６）を有し、
    　前記ピストンロッド（２０、２０Ａ、８２、８４、１０８、１６０）は、前記ピストン側係合部（４０、１６６）に係合したロッド側係合部（４２）を有し、
    　前記ピストン側係合部（４０、１６６）と前記ロッド側係合部（４２）は、一方の係合部が他方の係合部に側方から挿入されることにより、前記ピストン本体（３８、３８Ａ～３８Ｆ、１６２）と前記ピストンロッド（２０、２０Ａ、８２、８４、１０８、１６０）との軸方向の相対変位を規制するように係合している、
    　ことを特徴とするピストン組立体（１７Ａ～１７Ｍ）。     Piston bodies (38, 38A to 38F, 162) that are axially displaceable within the sliding holes (13, 103), and piston rods (axially protruding from the piston bodies (38, 38A to 38F, 162)) 20, 20A, 82, 84, 108, 160), and a piston assembly (17A-17M),
    The piston body (38, 38A to 38F, 162) has a piston side engaging portion (40, 166),
    The piston rod (20, 20A, 82, 84, 108, 160) has a rod side engaging portion (42) engaged with the piston side engaging portion (40, 166),
    The piston-side engaging portion (40, 166) and the rod-side engaging portion (42) are inserted into the other engaging portion from the side, so that the piston body (38, 38A-38F, 162) and the piston rod (20, 20A, 82, 84, 108, 160) are engaged so as to restrict relative displacement in the axial direction.
    A piston assembly (17A to 17M).
  2. 　請求項１記載のピストン組立体（１７Ａ～１７Ｍ）において、
    　前記ピストン側係合部（４０、１６６）及び前記ロッド側係合部（４２）の一方の係合部は、Ｕ字状、Ｃ字状又は半円弧状の係合溝（４４）を有し、
    　前記ピストン側係合部（４０、１６６）及び前記ロッド側係合部（４２）の他方の係合部は、前記係合溝（４４）に挿入された環状の係合突起（５６）を有する、
    　ことを特徴とするピストン組立体（１７Ａ～１７Ｍ）。     The piston assembly (17A-17M) according to claim 1,
    One engagement part of the piston side engagement part (40, 166) and the rod side engagement part (42) has a U-shaped, C-shaped or semi-arc shaped engagement groove (44). ,
    The other engaging portion of the piston side engaging portion (40, 166) and the rod side engaging portion (42) has an annular engaging protrusion (56) inserted into the engaging groove (44). ,
    A piston assembly (17A to 17M).
  3. 　請求項２記載のピストン組立体（１７Ａ～１７Ｍ）において、
    　前記係合溝（４４）は、前記ピストン側係合部（４０、１６６）に設けられており、
    　前記係合突起（５６）は、前記ロッド側係合部（４２）に設けられている、
    　ことを特徴とするピストン組立体（１７Ａ～１７Ｍ）。     The piston assembly (17A-17M) according to claim 2,
    The engagement groove (44) is provided in the piston side engagement portion (40, 166),
    The engaging protrusion (56) is provided on the rod side engaging portion (42).
    A piston assembly (17A to 17M).
  4. 　請求項１記載のピストン組立体（１７Ａ～１７Ｍ）において、
    　前記ピストン側係合部（４０、１６６）及び前記ロッド側係合部（４２）は、前記ピストン本体（３８、３８Ａ～３８Ｆ、１６２）の軸を中心に相対回転可能に係合している、
    　ことを特徴とするピストン組立体（１７Ａ～１７Ｍ）。     The piston assembly (17A-17M) according to claim 1,
    The piston side engaging portion (40, 166) and the rod side engaging portion (42) are engaged with each other so as to be relatively rotatable around the axis of the piston main body (38, 38A to 38F, 162).
    A piston assembly (17A to 17M).
  5. 　請求項１記載のピストン組立体において、
    　少なくとも一方のストロークエンド到達時の衝撃を緩和するダンパ機構（６０、６０Ａ）を備え、
    　前記ダンパ機構（６０、６０Ａ）は、ストロークエンド到達時に前記ピストン本体に衝撃荷重を伝達しないように前記ピストン本体に支持されている、
    　ことを特徴とするピストン組立体。     The piston assembly of claim 1, wherein
    Provided with a damper mechanism (60, 60A) for mitigating impact when reaching at least one stroke end,
    The damper mechanism (60, 60A) is supported by the piston body so as not to transmit an impact load to the piston body when reaching the stroke end.
    A piston assembly characterized by that.
  6. 　請求項５記載のピストン組立体において、
    　前記ダンパ機構（６０、６０Ａ）は、前記ピストンロッドの外周部に配置された外周側ダンパ（６２、１７０）を有し、
    　前記ピストンロッドの前記外周部には、周方向に延在するストッパ装着溝（７０）が設けられ、
    　前記ストッパ装着溝（７０）には、周方向に複数に分割されたストッパ部材（７２）が装着されており、
    　前記外周側ダンパ（６２、１７０）は前記ストッパ部材（７２）を覆っており、これにより、前記外周側ダンパ（６２、１７０）が前記ストッパ部材（７２）により支持されるとともに前記ストッパ部材（７２）が前記ストッパ装着溝（７０）から離脱することが阻止されている、
    　ことを特徴とするピストン組立体。     The piston assembly according to claim 5, wherein
    The damper mechanism (60, 60A) has an outer damper (62, 170) disposed on the outer periphery of the piston rod,
    A stopper mounting groove (70) extending in the circumferential direction is provided on the outer peripheral portion of the piston rod,
    In the stopper mounting groove (70), a stopper member (72) divided into a plurality in the circumferential direction is mounted,
    The outer periphery side dampers (62, 170) cover the stopper member (72), whereby the outer periphery side dampers (62, 170) are supported by the stopper member (72) and the stopper member (72). ) Is prevented from detaching from the stopper mounting groove (70),
    A piston assembly characterized by that.
  7. 　請求項５記載のピストン組立体において、
    　前記ダンパ機構（６０、６０Ａ）は、前記ピストンロッドの端面に配置された端部側ダンパ（６４、６４Ａ）を有し、
    　前記端部側ダンパ（６４、６４Ａ）は、前記ピストン本体と前記ピストンロッドとの間に保持されるとともに、前記ピストン本体の中心部に設けられた貫通孔（３８ａ、１６２ａ）から突出している、
    　ことを特徴とするピストン組立体。     The piston assembly according to claim 5, wherein
    The damper mechanism (60, 60A) includes an end side damper (64, 64A) disposed on an end surface of the piston rod,
    The end side dampers (64, 64A) are held between the piston main body and the piston rod, and protrude from through holes (38a, 162a) provided at the center of the piston main body.
    A piston assembly characterized by that.
  8. 　請求項７記載のピストン組立体において、
    　前記端部側ダンパ（６４、６４Ａ）は、前記ピストン本体と前記ピストンロッドとの間をシールしている、
    　ことを特徴とするピストン組立体。     The piston assembly according to claim 7,
    The end side damper (64, 64A) seals between the piston body and the piston rod,
    A piston assembly characterized by that.
  9. 　請求項７記載のピストン組立体において、
    　前記端部側ダンパ（６４、６４Ａ）は、前記ピストンロッドの前記端面を弾性的に押圧している、
    　ことを特徴とするピストン組立体。     The piston assembly according to claim 7,
    The end side damper (64, 64A) elastically presses the end face of the piston rod,
    A piston assembly characterized by that.
  10. 　請求項５記載のピストン組立体において、
    　前記ピストン本体は、樹脂製である、
    　ことを特徴とするピストン組立体。     The piston assembly according to claim 5, wherein
    The piston body is made of resin.
    A piston assembly characterized by that.
  11. 　請求項５記載のピストン組立体において、
    　前記ピストン本体には、前記ピストン側係合部（４０、１６６）を囲むとともに前記ピストン本体の軸方向に深さを有する肉抜き部（４６、５３）が設けられている、
    　ことを特徴とするピストン組立体。     The piston assembly according to claim 5, wherein
    The piston body is provided with a lightening portion (46, 53) that surrounds the piston side engaging portion (40, 166) and has a depth in the axial direction of the piston body.
    A piston assembly characterized by that.
  12. 　請求項１記載のピストン組立体（１７Ａ～１７Ｍ）において、
    　前記ピストン側係合部（４０、１６６）は、前記ピストン本体（３８、３８Ａ～３８Ｆ、１６２）の端面から軸方向に膨出するとともに軸方向から見てＵ字状に構成され、
    　前記ピストン側係合部（４０、１６６）の内周面には、Ｕ字状係合溝（４４）が設けられ、
    　前記ロッド側係合部（４２）は、前記Ｕ字状係合溝（４４）に挿入された環状の係合突起（５６）を有する、
    　ことを特徴とするピストン組立体（１７Ａ～１７Ｍ）。     The piston assembly (17A-17M) according to claim 1,
    The piston-side engaging portion (40, 166) is configured to be U-shaped when bulging in the axial direction from the end face of the piston main body (38, 38A to 38F, 162) and viewed from the axial direction,
    A U-shaped engaging groove (44) is provided on the inner peripheral surface of the piston side engaging portion (40, 166),
    The rod side engaging portion (42) has an annular engaging protrusion (56) inserted into the U-shaped engaging groove (44).
    A piston assembly (17A to 17M).
  13. 　請求項１記載のピストン組立体（１７Ｍ）において、
    　前記ピストンロッド（１６０）の外周部に配置され、ストロークエンド到達時の衝撃を緩和するリング状の外周側ダンパ（１７０）と、
    　前記ピストン本体（１６２）と前記外周側ダンパ（１７０）との間に介装されたリング状のスペーサ（１７２）とを備え、
    　前記ピストン本体（１６２）、前記スペーサ（１７２）及び前記外周側ダンパ（１７０）は軸方向に積層されている、
    　ことを特徴とするピストン組立体（１７Ｍ）。     Piston assembly (17M) according to claim 1,
    A ring-shaped outer damper (170) disposed on the outer periphery of the piston rod (160) to mitigate an impact when reaching the stroke end;
    A ring-shaped spacer (172) interposed between the piston body (162) and the outer damper (170);
    The piston main body (162), the spacer (172), and the outer peripheral side damper (170) are laminated in the axial direction.
    A piston assembly (17M).
  14. 　内部に摺動孔（１３、１０３）を有するボディと、前記摺動孔（１３、１０３）に沿って往復移動可能に配置されたピストン組立体（１７Ａ～１７Ｍ）とを備えた流体圧装置であって、
    　前記ピストン組立体（１７Ａ～１７Ｍ）は、前記摺動孔（１３、１０３）内を軸方向に変位可能なピストン本体（３８、３８Ａ～３８Ｆ、１６２）と、前記ピストン本体（３８、３８Ａ～３８Ｆ、１６２）から軸方向に突出したピストンロッド（２０、２０Ａ、８２、８４、１０８、１６０）とを備え、
    　前記ピストン本体（３８、３８Ａ～３８Ｆ、１６２）は、ピストン側係合部（４０、１６６）を有し、
    　前記ピストンロッド（２０、２０Ａ、８２、８４、１０８、１６０）は、前記ピストン側係合部（４０、１６６）に係合したロッド側係合部（４２）を有し、
    　前記ピストン側係合部（４０、１６６）と前記ロッド側係合部（４２）は、一方の係合部が他方の係合部に側方から挿入されることにより、前記ピストン本体（３８、３８Ａ～３８Ｆ、１６２）と前記ピストンロッド（２０、２０Ａ、８２、８４、１０８、１６０）との軸方向の相対変位を規制するように係合している、
    　ことを特徴とする流体圧装置。     A fluid pressure device including a body having a sliding hole (13, 103) inside, and a piston assembly (17A to 17M) arranged to be reciprocally movable along the sliding hole (13, 103). There,
    The piston assembly (17A to 17M) includes a piston body (38, 38A to 38F, 162) that can be displaced in the axial direction in the sliding hole (13, 103), and the piston body (38, 38A to 38F). 162) and a piston rod (20, 20A, 82, 84, 108, 160) protruding in the axial direction,
    The piston body (38, 38A to 38F, 162) has a piston side engaging portion (40, 166),
    The piston rod (20, 20A, 82, 84, 108, 160) has a rod side engaging portion (42) engaged with the piston side engaging portion (40, 166),
    The piston-side engaging portion (40, 166) and the rod-side engaging portion (42) are inserted into the other engaging portion from the side, so that the piston body (38, 38A-38F, 162) and the piston rod (20, 20A, 82, 84, 108, 160) are engaged so as to restrict relative displacement in the axial direction.
    A fluid pressure device.
  15. 　請求項１４記載の流体圧装置において、
    　前記流体圧装置は、流体圧シリンダ（１０Ａ～１０Ｄ）、バルブ装置、測長シリンダ、スライドテーブル又はチャック装置として構成されている、
    　ことを特徴とする流体圧装置。     The fluid pressure device according to claim 14.
    The fluid pressure device is configured as a fluid pressure cylinder (10A to 10D), a valve device, a length measuring cylinder, a slide table, or a chuck device.
    A fluid pressure device.
PCT/JP2017/040679 2016-12-06 2017-11-13 Piston assembly and fluid pressure device WO2018105314A1 (en)

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BR112019011573A BR112019011573A2 (en) 2016-12-06 2017-11-13 piston assembly and fluid pressure device
KR1020197019427A KR102201138B1 (en) 2016-12-06 2017-11-13 Piston assembly and fluid pressure device
RU2019120892A RU2737877C1 (en) 2016-12-06 2017-11-13 Piston assembly and hydraulic (pneumatic) device
US16/466,522 US11067173B2 (en) 2016-12-06 2017-11-13 Piston assembly and fluid pressure device
EP17878719.8A EP3553326A4 (en) 2016-12-06 2017-11-13 Piston assembly and fluid pressure device

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Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5147994Y2 (en) * 1972-04-11 1976-11-18
JPH0343139U (en) * 1989-09-01 1991-04-23
JPH05346106A (en) * 1992-06-10 1993-12-27 Aisan Ind Co Ltd Cylinder device
JP2014114874A (en) 2012-12-10 2014-06-26 Smc Corp Fluid pressure cylinder

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5147994Y2 (en) * 1972-04-11 1976-11-18
JPH0343139U (en) * 1989-09-01 1991-04-23
JPH05346106A (en) * 1992-06-10 1993-12-27 Aisan Ind Co Ltd Cylinder device
JP2014114874A (en) 2012-12-10 2014-06-26 Smc Corp Fluid pressure cylinder

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