JP2004011855A - Cylinder with speed control mechanism - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To control displacement speed of a piston in the whole region of stroke and miniaturize a cylinder in the longitudinal direction. <P>SOLUTION: This cylinder with a speed control mechanism is provided with: a cylinder body 16 having a first pressure fluid port 12 and a second pressure fluid port 14; the piston 22 provided inside it along the direction of axial line so as to displace freely; a rod main body 60 connected with the piston 22 integrally; a cylindrical body 44 connected with an end plug 18 in one end part of the cylinder body 16; a shaft member 64 connected with a rod end 62 in the other end part of the cylinder body 16 and provided inside the cylindrical body 44 so as to be inserted freely, a first cutout channel 46 formed on an outer peripheral face of the cylindrical body 44; and a second cutout channel 72 formed on an outer peripheral face of the shaft member 64. <P>COPYRIGHT: (C)2004,JPO

Description

[0001]
TECHNICAL FIELD OF THE INVENTION
The present invention relates to a cylinder with a speed control mechanism driven under the action of a pressurized fluid, and more particularly, to a cylinder with a speed control mechanism capable of freely changing a displacement speed in an entire region where a piston makes a stroke displacement.
[0002]
[Prior art]
2. Description of the Related Art Conventionally, for example, in a cylinder with a speed control mechanism, a piston is slidably provided in an axial direction inside a cylinder tube, and a pair of cover members is connected to both ends of the cylinder tube. The cover member is provided with a pair of hollow hollow holes so as to face each other, and a seal member for sealing an outer peripheral surface of a cushion ring described later is attached to an inner peripheral surface of the hollow hole. I have.
[0003]
At both ends of the piston, cushion rings protruding by a predetermined length in the axial direction are provided, and the cushion rings are inserted into the hollow holes of the cover member under the action of displacement of the piston.
[0004]
On the outer peripheral surface of the cushion ring, a so-called sine function groove is formed along the axial direction, and the sine function groove is formed so that the depth of the groove changes in a direction away from the piston of the cushion ring. .
[0005]
Under the action of the pressure fluid supplied from one fluid port, the piston is displaced while accelerating along the axial direction of the cylinder chamber, one cushion ring is inserted into a hollow hole of one cover member, and the cushion ring Is sealed by the seal member to reduce the displacement speed of the piston. Further, the piston is displaced while accelerating in the opposite direction along the axial direction under the action of the pressure fluid supplied from the other fluid port, and the other cushion ring is inserted into the hollow hole of the other cover member, and When the outer peripheral surface of the cushion ring is sealed by the seal member, the displacement speed of the piston is reduced again.
[0006]
[Problems to be solved by the invention]
By the way, in the cylinder with the speed control mechanism according to the prior art, the range in which the displacement speed of the piston can be controlled is a state in which a pair of cushion rings provided on both end surfaces of the piston are inserted into the hollow hole of the cover member. Therefore, the displacement speed when the piston is displaced between the cover members at the substantially central portion of the cylinder tube cannot be controlled.
[0007]
In other words, the displacement speed of the piston is controlled by inserting a cushion ring inside the hollow hole of the cover member under the action of displacement of the piston, so that the cushion ring of the piston is It is not possible to control the displacement speed when displacing more apart.
[0008]
Therefore, in order to be able to control the entire range of the stroke of the piston, it is conceivable to separately provide a speed control device such as a speed controller and control the displacement speed of the piston between a pair of cushion rings. However, there is a problem that connection of the speed control device and the like are complicated and costly.
[0009]
Further, when setting a wide range for controlling the displacement speed of the piston, it is necessary to increase the length of the cushion rings provided at both ends of the piston.
[0010]
Further, since it is necessary to provide a hollow hole through which the cushion ring is inserted inside the cover member, the axial length of the cover member in which the hollow hole is formed increases according to the length of the cushion ring. Therefore, there is a problem that the length of the entire cylinder in the longitudinal direction increases as the length of the cushion ring increases.
[0011]
The present invention has been made in consideration of the above-described various problems and the like, and can freely control the displacement speed of the piston over the entire stroke range along the axial direction of the piston. It is an object of the present invention to provide a cylinder with a speed control mechanism that can be implemented.
[0012]
[Means for Solving the Problems]
In order to achieve the above object, the present invention provides a cylinder body provided with a cylinder chamber closed by a cover member and having a set of ports for supplying a pressure fluid to the cylinder chamber, A cylinder having a piston, which is provided and is displaced along the axial direction in the cylinder chamber, and a piston rod integrally connected to the piston,
A cylindrical body disposed inside the cylinder body and connected to the cover member substantially in parallel with the piston rod;
A shaft member connected substantially parallel to the inside of the piston rod, and disposed so as to be freely inserted through the inside of the cylindrical body;
A first cutout groove formed in the outer peripheral surface of the cylindrical body along the axial direction;
A second cutout groove formed in the outer peripheral surface of the shaft member along the axial direction;
A first seal member surrounding an outer peripheral surface of the cylindrical body,
A second seal member surrounding an outer peripheral surface of the shaft member;
With
When the outer peripheral surface of the cylindrical body is surrounded by the first seal member, the flow rate of the pressure fluid flowing between the port and the cylinder chamber is controlled by the first notch groove, and / or When the outer peripheral surface is surrounded by the second seal member, the flow rate of the pressurized fluid flowing between the port and the cylinder chamber is controlled by the second cutout groove.
[0013]
According to the present invention, the first cutout groove is provided along the axial direction on the outer peripheral surface of the cylindrical body inside the cylinder body, and the second notch groove is provided along the axial direction on the outer peripheral surface of the shaft member passing through the inside of the cylindrical body. When a notch groove is provided and the outer peripheral surface of the cylindrical body is surrounded by the first seal member, the flow rate of the pressure fluid flowing between the port and the cylinder chamber is controlled by the first notch groove, and / or Alternatively, when the outer peripheral surface of the shaft member is surrounded by the second seal member, the flow rate of the pressure fluid flowing between the port and the cylinder chamber is controlled by the second cutout groove. Therefore, without providing a separate speed control device to control the displacement speed of the piston, the displacement speed of the piston can be suitably and simply controlled throughout the entire stroke range of the piston inside the cylinder, and the cost can be reduced. Can be reduced.
[0014]
In addition, the shaft member is provided so as to be housed inside the piston rod, and the cylindrical body is provided inside the cylinder body, so that the size in the longitudinal direction of the cylinder body is suppressed to reduce the size. Can be.
[0015]
Further, in the present invention, a cylinder chamber closed by a cover member is provided, a cylinder body having a set of ports for supplying a pressure fluid to the cylinder chamber, In a cylinder with a speed control mechanism having a piston displaced along an axial direction and a piston rod integrally connected to the piston,
A cylindrical body disposed inside the cylinder body and connected to the cover member substantially in parallel with the piston rod;
A shaft member connected substantially parallel to the inside of the piston rod, and disposed so as to be freely inserted through the inside of the cylindrical body;
A notch groove formed in the outer peripheral surface of the shaft member along the axial direction,
A seal member surrounding the outer peripheral surface of the shaft member;
With
When the outer peripheral surface of the shaft member is surrounded by the seal member, a flow rate of a pressurized fluid flowing between the port and the cylinder chamber is controlled by the cutout groove.
[0016]
According to the present invention, by providing a cutout groove along the axial direction on the outer peripheral surface of the shaft member provided so as to be freely inserted through the inside of the cylindrical body, when the outer peripheral surface of the shaft member is surrounded by the seal member, The flow rate of the pressure fluid flowing between the port and the cylinder chamber can be controlled. Therefore, the displacement speed of the piston inside the cylinder can be suitably and simply controlled, and the cost can be reduced.
[0017]
Further, in the present invention, a cylinder chamber closed by a cover member is provided, a cylinder body having a set of ports for supplying a pressure fluid to the cylinder chamber, and a cylinder body provided inside the cylinder body, and In a cylinder with a speed control mechanism having a piston displaced along an axial direction and a piston rod integrally connected to the piston,
A cylindrical body disposed inside the cylinder body and connected to the cover member substantially in parallel with the piston rod;
A notch groove formed along the axial direction on the outer peripheral surface of the cylindrical body,
A sealing member surrounding the outer peripheral surface of the cylindrical body,
With
When the outer peripheral surface of the cylindrical body is surrounded by the seal member, a flow rate of a pressure fluid flowing between the port and the cylinder chamber is controlled by the cutout groove.
[0018]
According to the present invention, when the outer peripheral surface of the cylindrical body is surrounded by the seal member, the port and the cylinder chamber are provided by providing a cutout groove along the axial direction on the outer peripheral surface of the cylindrical body inside the cylinder body. Can be controlled. Therefore, the displacement speed of the piston inside the cylinder can be suitably and simply controlled, and the cost can be reduced.
[0019]
Furthermore, by forming the first notch groove and / or the second notch groove such that the depth of the groove gradually increases in the direction from the piston rod toward the piston, the depth of the groove varies depending on the depth of the groove. Since the flow rate of the pressure fluid flowing through the inside of the first notch groove and / or the second notch groove can be changed, the piston is gradually decelerated when displaced along the axial direction of the piston. The cylinder can be more smoothly displaced.
[0020]
Furthermore, by forming the first notch groove and / or the second notch groove such that the depth of the groove gradually increases toward the central portion along the axial direction of the cylindrical body and / or the shaft member, By changing the flow rate of the pressure fluid flowing inside the first notch groove and / or the second notch groove according to the depth of the groove, the piston approaches the initial position and the displacement end position along the axial direction of the piston. At this time, the displacement speed of the piston can be gradually reduced.
[0021]
Further, since the first notch groove and / or the second notch groove is formed in a multi-step shape of a plurality of grooves having different depths, the first notch groove and / or the second notch groove and / or the second notch groove are formed in accordance with the depth of the multi-step groove. The displacement speed of the piston can be controlled stepwise by changing the flow rate of the pressure fluid flowing inside the second cutout groove.
[0022]
Furthermore, by forming the depth of the notch groove so as to gradually increase from the piston rod toward the piston, the pressure fluid flowing through the notch groove according to the depth of the groove is formed. By changing the flow rate, when the piston is displaced along the axial direction of the piston, the acceleration and deceleration of the piston can be gradually performed, and the cylinder can be displaced more smoothly.
[0023]
Still further, the notch groove is formed so that the depth of the groove gradually increases toward the central portion along the axial direction of the cylindrical body and / or the shaft member, so that the depth of the groove increases in accordance with the depth of the groove. Since the flow rate of the pressure fluid flowing through the inside of the notch groove can be changed, the displacement speed of the piston can be gradually reduced when approaching the initial position and the displacement end position along the axial direction of the piston.
[0024]
Further, the notch groove is formed in a multi-step shape having a plurality of different groove depths, thereby changing a flow rate of a pressure fluid flowing through the inside of the notch groove according to the depth of the multi-step groove. Therefore, the displacement speed of the piston can be controlled stepwise.
[0025]
BEST MODE FOR CARRYING OUT THE INVENTION
A preferred embodiment of a cylinder with a speed control mechanism according to the present invention will be described below in detail with reference to the accompanying drawings.
[0026]
1 and 2, reference numeral 10 indicates a cylinder with a speed control mechanism according to the first embodiment of the present invention.
[0027]
The cylinder 10 with a speed control mechanism includes a cylinder body 16 in which first and second pressure fluid ports 12 and 14 to which a pressure fluid is supplied are formed, and an end plug (a cover member) attached to one end of the cylinder body 16. ) 18, an end block (cover member) 20 connected to the other end of the cylinder body 16, a piston 22 disposed inside the cylinder body 16 so as to be displaceable in the axial direction, and the piston And a rod (piston rod) 24 connected to the rod 22.
[0028]
On the upper surface of the cylinder body 16, a first pressure fluid port 12 through which a pressure fluid is supplied from a pressure fluid supply source (not shown) to the inside of the cylinder body 16 is formed on the end plug 18 side. The port 14 is formed on the end block 20 side.
[0029]
At a substantially central portion of the cylinder body 16, a through hole 26 is formed along the axial direction. The end plug 18 is inserted into the through hole 26 on one end side of the cylinder body 16, and the flange portion 28 whose diameter is increased in the radially outward direction is engaged with the step portion 30 of the through hole 26 and positioned at a predetermined position. . After the end plug 18 is inserted into the through hole 26, the stopper ring 32 is attached to an annular groove formed near the opening of the through hole 26, thereby preventing the end plug 18 from being pulled out. That is, the displacement of the end plug 18 in the axial direction is restricted by the flange portion 28 and the stopper ring 32.
[0030]
In addition, a pair of seal members 34 are mounted on the outer peripheral surface of the end plug 18 via an annular groove at two locations separated by a predetermined distance, so that the inside of the through hole 26 is kept airtight. A communication groove 38 communicating with the first pressure fluid port 12 via the communication passage 36a is recessed by a predetermined length and formed annularly between the pair of seal members 34 on the outer peripheral surface of the end plug 18. The communication groove 38 is formed along the outer peripheral surface of the end plug 18 and communicates with a plurality of first passages 40 extending in a direction substantially perpendicular to the axis.
[0031]
A buffer member 42a is mounted on an end surface of the end plug 18 facing the one end surface of the piston 22 through an annular groove, and the buffer member 42a is formed of an elastic member such as rubber. In addition, the impact when the one end surface of the piston 22 comes into contact with the end surface of the end plug 18 can be reduced.
[0032]
One end of a long cylindrical body 44 is fitted into a substantially central portion of the end plug 18, and is integrally connected so as to protrude toward the end block 20. A seal member 34 is mounted on the outer periphery of the cylindrical body 44 and keeps the inside of the through hole 26 airtight by contacting the inner peripheral surface of the end plug 18.
[0033]
As shown in FIG. 1, the cylindrical body 44 has an end surface 45 on the inner side of the rod end 62 and an end surface of the cylindrical body 44 in an initial position where one end surface of the piston 22 is in contact with the buffer member 42a. Not set to a length.
[0034]
On the outer periphery of the cylindrical body 44, a first cutout groove 46 having a substantially rectangular cross section, which is recessed by a predetermined length, is formed linearly along the axial direction (see FIG. 3). The depth of the first notch groove 46 is formed so as to gradually increase toward the end plug 18 side (the direction of arrow B) (see FIG. 5). Note that the width of the first notch groove 46 in the width direction is constant (see FIG. 3).
[0035]
Further, as shown in FIG. 1, a second passage 48 communicating with the first passage 40 of the end plug 18 is formed at one end of the cylindrical body 44, and the first pressure is formed through the second passage 48. The pressure fluid supplied from the fluid port 12 is provided so as to be introduced into the cylindrical body 44.
[0036]
The end block 20 having a substantially T-shaped cross section is integrally connected to the other end of the cylinder body 16, and a projecting portion 50 is formed at a substantially central portion of the end block 20 so as to project toward the cylinder body 16. 26 is fitted into the end. A seal member 34 is mounted on the outer periphery of the protruding portion 50 through an annular groove to keep the inside of the through hole 26 airtight.
[0037]
The piston 22 is formed in a substantially cylindrical shape, the outer peripheral surface of the piston 22 slides along the inner peripheral surface of the through hole 26 of the cylinder body 16, and the inner peripheral surface of the piston 22 is the outer peripheral surface of the cylindrical body 44. It is arranged so as to be separated by a predetermined distance. That is, the piston 22 functions as the first and second cylinder chambers that function as a cylinder chamber under the action of guiding the inner peripheral surface of the cylinder body 16 under the action of the pressure fluid supplied from the first pressure fluid port 12 or the second pressure fluid port 14. It is displaced along the axial direction of the second chambers 52, 54 (described later).
[0038]
A first chamber 52 is formed between one end surface of the piston 22 and the end plug 18 in the cylinder body 16, and a first chamber 52 is formed between the other end surface of the piston 22 and the end surface of the protruding portion 50 of the end block 20. A second chamber 54 is formed between them. The second chamber 54 communicates with the second pressure fluid port 14 via a communication passage 36b.
[0039]
Further, a throttle passage 55 may be provided between the first chamber 52 and the first pressure fluid port 12 so that the flow rate of the flowing pressure fluid is reduced by a predetermined amount. The throttle function of the flow rate of the pressure fluid flowing through the throttle passage 55 may be such that the flow rate of the pressure fluid supplied from the first pressure fluid port 12 to the first chamber 52 is reduced, or conversely, the first flow rate is reduced. The flow rate of the pressure fluid led out from the chamber 52 to the first pressure fluid port 12 may be reduced. The throttle amount of the pressure fluid flowing through the throttle passage 55 is provided so as to be arbitrarily adjustable from outside using, for example, an adjustment screw (not shown).
[0040]
A piston packing 56 is mounted on the outer peripheral surface of the piston 22 through an annular groove, and a wear ring 58 is mounted at a predetermined interval from the piston packing 56, and the first chamber 52 and the second chamber 52 are mounted. , Respectively.
[0041]
A check packing (first sealing member) 59 is in contact with the outer peripheral surface of the cylindrical body 44 via an annular groove on the inner peripheral surface of the piston 22, and is moved from a third chamber 74 described later to the first chamber 52. The third chamber 74 and the first chamber 52, which will be described later, are in communication with each other only through the first cutout groove 46 of the cylindrical body 44 (see FIG. 3). . That is, since the depth of the first notch groove 46 at the position facing the check packing 59 changes depending on the displacement position of the check packing 59 displaced integrally with the piston 22, the depth of the first notch groove 46 is changed via the first notch groove 46. The flow rate of the pressurized fluid flowing between the third and first chambers 74, 52 changes accordingly.
[0042]
Further, an annular buffer member 42b is mounted on the other end surface of the piston 22, and the buffer member 42b is formed of an elastic member such as rubber. The impact at the time of contacting the end face of the portion 50 is reduced.
[0043]
A rod body 60 of the rod portion 24 is integrally connected to a substantially central portion of the piston 22 toward the end block 20 via a screw portion.
[0044]
The rod portion 24 includes a cylindrical rod body 60 having one end integrally connected to the piston 22, a rod end 62 integrally screwed to the other end of the rod body 60, A shaft member 64 connected substantially in parallel with the rod body 60 is provided substantially at the center of the shaft 62.
[0045]
The rod main body 60 is formed in a long shape, and one end is screwed to a substantially central portion of the piston 22, and the other end is screwed to the outer peripheral surface of the rod end 62. That is, the rod body 60 is displaced integrally with the piston 22 and the rod end 62 along the axial direction. Inside the rod body 60, a third chamber 74 is defined between the rod end 62 and the other end surface of the piston 22, and a seal mounted on the inner peripheral surface of the piston 22 to which the rod body 60 is screwed. The member 34 keeps the second chamber 54 and the third chamber 74 airtight.
[0046]
Further, the other end of the rod body 60 is slidably supported inside the end block 20, and a rod packing 66 is mounted on an inner peripheral surface of the end block 20 supporting the rod body 60 via an annular groove. The bush 68 is provided at a predetermined interval. Therefore, the airtightness inside the second chamber 54 is reliably maintained.
[0047]
A connecting member 70 is attached to a substantially central portion of the rod end 62 via a hole 69, and a long shaft member 64 is integrally connected to the connecting member 70 via a screw member 71. The shaft member 64 is connected so as to be housed inside the rod body 60. In an initial position where one end surface of the shaft member 64 and the piston 22 abuts on the buffer member 42a, the tip end of the shaft member 64 is connected to the end plug 18. At a displacement end position where the other end surface of the piston 22 is in contact with the end block 20, the length is set so that the distal end of the shaft member 64 does not come out of the cylindrical body 44. Is done.
[0048]
In addition, a second cutout groove 72 having a substantially rectangular cross-section recessed by a predetermined length is formed linearly along the axial direction on the outer periphery of the shaft member 64 (see FIGS. 3 and 4). The depth of the second cutout groove 72 is formed so as to gradually increase toward the end plug 18 side of the shaft member 64. The dimension of the second notch groove 72 in the width direction is formed to be constant (see FIG. 3).
[0049]
The shaft member 64 is provided so as to be freely inserted into the cylindrical body 44, and the outer peripheral surface of the shaft member 64 is provided at a predetermined distance from the inner peripheral surface of the cylindrical body 44 (see FIG. 3).
[0050]
A fourth chamber 76 is formed between the end face 75 of the shaft member 64 and the inside of the cylindrical body 44, and the first pressure fluid port 12 is formed through the communication passage 36 a and the first and second passages 40 and 48. Is in communication with A check packing (second seal member) 78 is attached to the end of the cylindrical body 44 on the rod end 62 side through an annular groove on the inner peripheral surface, and the check packing 78 is inserted into the inside of the cylindrical body 44. The third chamber 74 and the fourth chamber 76 are mounted on the shaft member 64 so as to be in contact with the outer peripheral surface of the shaft member 64 and to be sealed from the third chamber 74 toward the fourth chamber 76. It is in a state of communicating only through the second notch groove 64 of FIG.
[0051]
That is, since the depth of the second notch groove 72 at the position facing the check packing 78 changes depending on the displacement position of the shaft member 64, the third chamber 74 and the fourth chamber 74 are connected via the second notch groove 72. The flow rate of the pressure fluid flowing between the chambers 76 changes accordingly.
[0052]
The cylinder 10 with the speed control mechanism according to the first embodiment of the present invention is basically configured as described above. Next, the operation and effect of the cylinder will be described.
[0053]
As shown in FIG. 1, in the initial position, the first pressure fluid port 12 and the second pressure fluid port 14 are connected to a pressure fluid supply source (not shown) via a tube (not shown).
[0054]
Then, a pressure fluid (for example, compressed air) is supplied from the pressure fluid supply source to the first pressure fluid port 12 via the tube. The pressure fluid supplied from the first pressure fluid port 12 is introduced into the fourth chamber 76 in the cylindrical body 44 from the communication passage 36a through the communication groove 38, the first and second passages 40 and 48, and the shaft member. 64 is pressed in the direction of arrow A. Note that, in this case, the pressure fluid may be supplied to the first chamber 52 via the throttle passage 55 and the one end surface of the piston 22 may be pressed, so that the displacement speed of the piston 22 may be further increased.
[0055]
As a result, the rod body 60 and the piston 22 are integrally displaced in the direction of arrow A along the axial direction via the rod end 62 to which the shaft member 64 is connected.
[0056]
Then, the pressure fluid introduced into the fourth chamber 76 is introduced into the third chamber 74 in the rod body 60 via the second cutout groove 72 of the shaft member 64 and the opening of the check packing 78.
[0057]
At this time, the pressure fluid introduced into the third chamber 74 is introduced into the first chamber 52 through the first cutout groove 46 of the cylindrical body 44, and the piston 22 is displaced while accelerating the piston 22 in the direction of arrow A. Let it.
[0058]
Since the first notch groove 46 of the cylindrical body 44 is formed so as to be gradually deeper toward the end plug 18, the piston 22 is displaced in the direction away from the end plug 18 (the direction of arrow A). Accordingly, the cross-sectional area of the first notch groove 46 at the position facing the check packing 59 gradually decreases, and the flow rate of the pressure fluid introduced from the third chamber 74 to the first chamber 52 gradually decreases. I do. Therefore, the pressing force applied to one end surface of the piston 22 gradually decreases, and the displacement speed of the piston 22 gradually decreases.
[0059]
Lastly, the buffer member 42b mounted on one end surface of the piston 22 comes into contact with the end surface of the protruding portion 50, thereby setting the displacement end position (see FIG. 2). At this time, the shock when the piston 22 abuts on the end face of the protruding portion 50 is suitably reduced by the buffer member 42b. At this time, the fluid inside the second chamber 54 is discharged to the outside from the second pressure fluid port 14 via the communication passage 36b.
[0060]
Next, when the piston 22 is displaced in the direction of arrow B, a pressure fluid is supplied to the second pressure fluid port 14 from a pressure fluid supply source (not shown). At this time, the first pressure fluid port 12 and the fourth chamber 76 are set to the atmosphere open state communicating with the outside. As shown in FIG. 2, the pressure fluid supplied from the second pressure fluid port 14 is introduced into the second chamber 54 in the cylinder body 16 through the communication passage 36b, and the other end face of the piston 22 is pointed by an arrow B. By pressing in the direction, the rod body 60 and the rod end 62 are integrally displaced in the direction of arrow B along the axial direction via the piston 22.
[0061]
At that time, the pressure fluid introduced into the first chamber 52 and the third chamber 74 when the piston 22 is displaced in the direction of the arrow A is led out to the fourth chamber 76 through the second cutout groove 72, It is led out from the first pressure fluid port 12 through the first and second passages 40 and 48 and the communication passage 36a. In this case, the pressure fluid in the first chamber 52 is drawn out from the first pressure fluid port 12 through the throttle passage 55, and the displacement speed of the piston 22 along the arrow B direction is further increased. Good.
[0062]
At the initial position where the piston 22 is displaced in the direction of arrow B, the cross-sectional area of the second cutout groove 72 at the position facing the check packing 78 of the cylindrical body 44 is large, so that the third chamber 74 moves to the fourth chamber 76. The flow rate of the derived pressure fluid is large. Therefore, the pressure fluid remaining in the third chamber 74 is preferably led out to the fourth chamber 76 through the second cutout groove 72 under the action of the displacement of the piston 22, and the displacement of the piston 22 becomes resistance. The piston 22 is displaced in the direction of the arrow B while accelerating without acceleration. Since the cross-sectional area of the second notch groove 72 at the position facing the check packing 78 under the displacement action of the piston 22 gradually decreases, the first chamber 52 and the third chamber 74 to the fourth chamber 74 The flow rate of the pressure fluid led to 76 gradually decreases.
[0063]
As a result, the displacement speed of the piston 22 gradually decreases.
[0064]
Then, as the pressurized fluid inside the third chamber 74 is gradually led out, one end surface of the piston 22 comes into contact with the buffer member 42a mounted on the end surface of the end plug 18, and the displacement end position is reached (FIG. 1). At this time, the shock when the piston 22 abuts on the end face of the end plug 18 is suitably reduced by the buffer member 42a.
[0065]
As described above, in the first embodiment, the first notch groove 46 and the second notch groove 72 are provided on the outer peripheral surfaces of the cylindrical body 44 and the shaft member 64, respectively, and the first notch groove 46 and the second notch groove are provided. By setting the depth of each of the grooves 72 so as to gradually increase toward the end plug 18, the displacement speed of the piston 22 along the axial direction can be controlled to be reduced.
[0066]
Further, since the displacement speed of the piston 22 can be controlled by the first notch groove 46 and the second notch groove 72 over the entire stroke range of the piston 22 inside the cylinder body 16, it is not necessary to separately set an apparatus. Therefore, complicated work such as connection of the speed control device is not required, and the cost can be reduced.
[0067]
Further, since the cylindrical body 44 and the shaft member 64 in which the first notch groove 46 and the second notch groove 72 are formed for controlling the displacement speed of the piston 22 are housed inside the rod body 60, respectively, Without increasing the size of the entire device including the cylinder body 16 in the longitudinal direction.
[0068]
Next, a cylinder 100 with a speed control mechanism according to a second embodiment is shown in FIG. In the following second and third embodiments, the same components as those of the cylinder 10 with the speed control mechanism according to the above-described first embodiment are denoted by the same reference numerals, and details thereof will be described. Detailed description is omitted.
[0069]
In the cylinder with a speed control mechanism 100 according to the second embodiment, as shown in FIG. 6, instead of the throttle passage 55 provided between the first pressure fluid port 12 and the first chamber 52, A second pressure fluid port 102 is provided adjacent to the first pressure fluid port 12, and the second pressure fluid port 102 is communicated with the first chamber 52 through the communication passage 36b. The point that only the notch groove 104 is provided on the outer peripheral surface of the shaft member 64 without providing the first notch groove 46 and the air hole 106 that connects the inside and the outside of the rod body 60 is provided, as shown in FIG. As described above, the notch groove 104 is formed such that the shape of the groove gradually increases from both ends of the shaft member 64 toward the substantially central portion, and the substantially central portion along the axial direction is the deepest. Also piston The O-rings 108a and 108b are mounted instead of the check packings 59 and 78 mounted on the inner peripheral surface and the inner peripheral surface of the cylindrical body 44. Are different. The widthwise dimension of the notch groove 104 is formed to be constant.
[0070]
In this case, as shown in FIG. 6, both the displacement speed of the piston 22 when the piston 22 reciprocates in the directions of the arrows A and B by the pressure fluid flowing through the notch groove 104 is controlled by the notch groove 104. ing.
[0071]
When the pressure fluid is supplied from the second pressure fluid port 102, the piston 22 is displaced in the direction of arrow A under the pressing action of the pressure fluid supplied to the first chamber 52. At this time, the fluid inside the second chamber 54 is led to the third chamber 74 via the air hole 106 of the rod body 60, and the fourth chamber 76 is provided between the O-ring 108b and the notch groove 104. And discharged from the first pressure fluid port 12 to the outside.
[0072]
Further, at this time, when the substantially central portion of the shaft member 64 where the notch groove 104 is deepest is displaced to a position facing the O-ring 108b of the cylindrical body 44, the cross-sectional area of the notch groove 104 becomes maximum, The flow rate of the fluid discharged from the pressure fluid port 12 is increased, and the displacement speed of the piston 22 is maximized.
[0073]
Then, when the piston 22 is further displaced in the direction of arrow A, the cross-sectional area of the cutout groove 104 at the position facing the O-ring 108b of the cylindrical body 44 starts to decrease again, and is discharged from the first pressure fluid port 12. The flow rate of the fluid decreases and the piston 22 decelerates.
[0074]
Further, when the pressure fluid is supplied from the first pressure fluid port 12 in a state where the piston 22 is in contact with the protrusion 50 of the end block 20, the pressure fluid introduced into the fourth chamber 76 flows through the notch groove 104. And is introduced into the third chamber 74. The pressure fluid introduced into the third chamber 74 is introduced into the second chamber 54 through the air hole 106 of the rod body 60. The piston 22 is displaced in the direction of the arrow B under the action of the pressure fluid introduced into the second chamber 54. At this time, the fluid inside the first chamber 52 is discharged from the second pressure fluid port 102 to the outside.
[0075]
As the piston 22 is displaced in the direction of the arrow B, the notch groove 104 is displaced to a position where the substantially central portion of the shaft member 64 where the groove depth is deepest faces the O-ring 108 b of the cylindrical body 44. Since the cross-sectional area of the notch groove 104 is maximized, the flow rate of the pressurized fluid introduced into the second chamber 54 is further increased. As a result, the displacement speed of the piston 22 becomes the highest.
[0076]
Then, when the piston 22 is further displaced in the direction of arrow B, the cross-sectional area of the cutout groove 104 at the position facing the O-ring 108b of the cylindrical body 44 starts to decrease again. The flow rate of the pressure fluid introduced into 54 decreases, and piston 22 gradually decelerates.
[0077]
As a result, by providing the notch groove 104 that gradually becomes deeper from both ends of the shaft member 64 toward the substantially central portion, the piston 22 is displaced while gradually accelerating from the initial position, and is displaced in the substantially central portion of the cylinder body 16. As the displacement speed becomes the highest, the speed can be gradually reduced from there, and the displacement speed of the piston 22 can be freely controlled.
[0078]
Next, a cylinder 150 with a speed control mechanism according to a third embodiment is shown in FIG.
[0079]
In the cylinder 150 with the speed control mechanism according to the third embodiment, as shown in FIG. 8, the shaft body 64 connected to the rod end 62 via the connecting member 70 is not provided, and A fifth chamber 152 in which a third chamber 74 formed inside and a fourth chamber 76 formed inside the cylinder 44 are integrally formed, and the outer periphery of the cylinder 44 Only the notch groove 154 is provided on the surface, and the shape of the notch groove 154 is gradually deepened from both ends of the cylindrical body 44 toward the substantially central portion, and the depth of the groove is the most at the substantially central portion along the axial direction. A cylinder with a speed control mechanism according to the first embodiment in that it is formed so as to be deeper and that an O-ring 156 is provided instead of the check packing 59 mounted on the inner peripheral surface of the piston 22. It is different from 10. In addition, the widthwise dimension of the notch groove 154 is formed to be constant.
[0080]
In this case, the notch groove 154 controls the displacement speed of the piston 22 when the piston 22 reciprocates in the directions of arrows A and B by the pressure fluid flowing through the notch groove 154.
[0081]
When the pressure fluid is supplied from the first pressure fluid port 12, the pressure fluid is introduced into the fifth chamber 152 formed inside the cylindrical body 44, and the pressure fluid introduced into the fifth chamber 152 is notched. It is gradually introduced into the first chamber 52 through the groove 154. Then, by pressing one end surface of the piston 22 in the direction of arrow A, the piston 22 is displaced in the direction of arrow A along the axial direction. When the substantially central portion of the cylindrical body 44 where the notch groove 154 has the deepest groove is displaced to a position facing the O-ring 156 on the inner peripheral surface of the piston 22, the cross-sectional area of the notch groove 154 becomes maximum. The displacement speed of the piston 22 becomes the highest.
[0082]
Then, when the piston 22 is further displaced in the direction of the arrow A, the cross-sectional area of the cutout groove 154 at the position facing the O-ring 156 of the piston 22 starts to decrease again, so that the piston 22 gradually decelerates.
[0083]
As a result, by providing the cutout groove 154 so that the depth of the groove gradually increases from both ends of the cylindrical body 44 toward the substantially central portion, the piston 22 is displaced while gradually accelerating, and further from there. Displace while gradually decelerating. Therefore, the displacement speed of the piston 22 can be freely controlled.
[0084]
Further, since the shaft member 64 and the connecting member 70 are not required, the structure can be simplified and the cost can be reduced.
[0085]
Next, the shape of the notch groove 200 according to the modification will be described. Note that the cutout groove 200 according to the modification is not limited to being provided on the outer peripheral surface of the shaft member 64, and may be provided only on the outer peripheral surface of the cylindrical body 44, or may be provided on the shaft member 64 and the cylindrical body 44. You may make it provide in both simultaneously.
[0086]
As shown in FIG. 9, the notch groove 200 has a first groove 202, a second groove 204, and a third groove 206 having different groove depths toward the end plug 18 side of the shaft member 64, respectively. Between the first groove portion 202, the second groove portion 204, and the third groove portion 206, shallow groove portions 208a, 208b each having a depth smaller than that of the first to third groove portions 202, 204, 206 are formed. I have. Further, the size of the notch groove 200 in the width direction is formed to be constant.
[0087]
Between the first to third groove portions 202, 204, 206 and the shallow groove portions 208a, 208b, inclined surfaces 210a to 210d inclined at a predetermined angle are formed. That is, the notch groove 200 is formed in a multi-stage shape by the first to third groove portions 202, 204, 206 and the shallow groove portions 208a, 208b.
[0088]
Note that the depth, position, length, and the like of the first to third groove portions 202, 204, 206 and the shallow groove portions 208a, 208b are not limited thereto. Further, the number of grooves provided in the notch groove 200 is not limited to this, and may be arbitrarily set according to the use of the cylinders 10, 100, and 150 with a speed control mechanism.
[0089]
The first to third grooves 202, 204, and 206 are formed so as to become deeper in the order of depth C, depth D, and depth E substantially in parallel with the axis of the shaft member 64 (C <D). <E). Similarly, the shallow groove portions 208a and 208b are formed substantially in parallel with the axis of the shaft member 64.
[0090]
As a result, by forming the notch groove 200 into a multi-stage shape in which the depths of the first to third groove portions 202, 204, 206 and the shallow groove portions 208a, 208b are respectively different, the pressure fluid flowing through the notch groove 200 The flow rate can be changed stepwise. Therefore, the displacement speed of the piston 22 that is displaced under the pressing action of the pressure fluid can be accelerated or decelerated stepwise according to the depth of the groove.
[0091]
Specifically, for example, as shown in FIG. 6, when the pressure fluid is exhausted to the outside from the first pressure fluid port 12 (see FIG. 1), the shaft member 64 is integrated with the piston 22 in the arrow A direction. When the first groove portion 202 (see FIG. 9) is displaced to a position facing the O-ring 108b of the cylindrical body 44 when displaced, the pressure from the second chamber 54 and the third chamber 74 via the first groove portion 202 is increased. Fluid is introduced into the fourth chamber 76. The piston 22 is displaced while accelerating in the direction of arrow A by the exhaust flow rate of the pressure fluid. Further, when the shaft member 64 is displaced integrally with the piston 22 and the shallow groove portion 208a (see FIG. 9) is displaced to a position facing the O-ring 108b, the groove is gradually formed from the inclined surface 210a to the shallow groove portion 208a. Since the depth becomes shallow, the flow rate of the pressure fluid flowing through the notch groove 200 (see FIG. 9) gradually decreases. Therefore, the displacement speed of the shaft member 64 gradually decreases. When the shaft member 64 is further displaced and displaced via the inclined surface 210b to a position facing the second groove portion 204 (see FIG. 9), the cross-sectional area of the notch groove 200 increases again, so that the flow rate of the pressure fluid is reduced. It gradually increases, and the shaft member 64 is displaced along the axial direction while gradually accelerating. At this time, the displacement speed of the shaft member 64 and the piston 22 is higher than the displacement speed when the first groove portion 202 faces the O-ring 108b.
[0092]
After the displacement speed of the shaft member 64 is gradually reduced by again facing the shallow groove portion 208b (see FIG. 9) via the inclined surface 210c, the third groove portion 206 (see FIG. 9) via the inclined surface 210d. , The flow rate of the pressure fluid increases again, so that the shaft member 64 starts to gradually accelerate.
[0093]
That is, the depth of the first to third groove portions 202, 204, 206, the shallow groove portions 208a, 208b, that is, the groove depth of the notch groove 200 is set according to the intended use of the cylinders 10, 100, 150 with a speed control mechanism. Thus, the displacement speed of the piston 22 can be freely changed.
[0094]
【The invention's effect】
According to the present invention, the following effects can be obtained.
[0095]
That is, by providing the cylinder with a speed control mechanism that controls the displacement speed of the piston that displaces the inside of the cylinder body, the piston displacement speed can be freely controlled over the entire range of the stroke of the piston. Can be suitably and simply controlled, and the cost can be reduced.
[Brief description of the drawings]
FIG. 1 is a longitudinal sectional view of a cylinder with a speed control mechanism according to a first embodiment of the present invention at an initial piston position.
FIG. 2 is a longitudinal sectional view of the cylinder with a speed control mechanism according to the first embodiment of the present invention at a piston displacement end position.
FIG. 3 is a longitudinal sectional view taken along line III-III in FIG.
FIG. 4 is a partially omitted perspective view of a shaft member of the cylinder with a speed control mechanism according to the first embodiment of the present invention.
FIG. 5 is a partially omitted enlarged view of first and second cutout grooves of the cylinder with a speed control mechanism according to the first embodiment of the present invention.
FIG. 6 is a longitudinal sectional view of a cylinder with a speed control mechanism according to a second embodiment of the present invention.
FIG. 7 is a partially omitted enlarged view of a cutout groove of a cylinder with a speed control mechanism according to a second embodiment of the present invention.
FIG. 8 is a longitudinal sectional view of a cylinder with a speed control mechanism according to a third embodiment of the present invention.
FIG. 9 is a partially omitted enlarged view of a cutout groove according to a modified example.
[Explanation of symbols]
10, 100, 150 ... cylinder with speed control mechanism
12 ... first pressure fluid port 14, 102 ... second pressure fluid port
16 ... Cylinder body 18 ... End plug
20 ... End block 22 ... Piston
24: rod part 44: cylindrical body
46: first notch groove 52: first chamber
54: second chamber 59, 78: check packing
60: Rod body 62: Rod end
64: shaft member 72: second cutout groove
74 ... third room 76 ... fourth room
152: Fifth chamber 202: First groove
204: second groove 206: third groove
208a, 208b ... shallow groove

Claims (9)

A cylinder chamber closed by a cover member is provided, a cylinder body having a set of ports for supplying a pressure fluid to the cylinder chamber, and a cylinder body provided inside the cylinder body and displaced in the cylinder chamber along an axial direction. And a cylinder having a piston rod integrally connected to the piston,
A cylindrical body disposed inside the cylinder body and connected to the cover member substantially in parallel with the piston rod;
A shaft member connected substantially parallel to the inside of the piston rod, and disposed so as to be freely inserted through the inside of the cylindrical body;
A first cutout groove formed in the outer peripheral surface of the cylindrical body along the axial direction;
A second cutout groove formed in the outer peripheral surface of the shaft member along the axial direction;
A first seal member surrounding an outer peripheral surface of the cylindrical body,
A second seal member surrounding an outer peripheral surface of the shaft member;
With
When the outer peripheral surface of the cylindrical body is surrounded by the first seal member, the flow rate of the pressure fluid flowing between the port and the cylinder chamber is controlled by the first notch groove, and / or When the outer peripheral surface is surrounded by the second seal member, the flow rate of the pressure fluid flowing between the port and the cylinder chamber is controlled by the second cutout groove, wherein the cylinder has a speed control mechanism. A cylinder chamber closed by a cover member is provided, a cylinder body having a set of ports for supplying a pressure fluid to the cylinder chamber, and a cylinder body provided inside the cylinder body and displaced in the cylinder chamber along an axial direction. A piston having a piston and a piston rod integrally connected to the piston, a cylinder disposed in the cylinder body and connected to the cover member substantially in parallel with the piston rod;
A shaft member connected substantially parallel to the inside of the piston rod, and disposed so as to be freely inserted through the inside of the cylindrical body;
A notch groove formed in the outer peripheral surface of the shaft member along the axial direction,
A seal member surrounding the outer peripheral surface of the shaft member;
With
When the outer peripheral surface of the shaft member is surrounded by the seal member, a flow rate of a pressurized fluid flowing between the port and the cylinder chamber is controlled by the notch groove. A cylinder chamber closed by a cover member is provided, a cylinder body having a set of ports for supplying a pressure fluid to the cylinder chamber, and a cylinder body provided inside the cylinder body and displaced in the cylinder chamber along an axial direction. And a cylinder having a piston rod integrally connected to the piston,
A cylindrical body disposed inside the cylinder body and connected to the cover member substantially in parallel with the piston rod;
A notch groove formed along the axial direction on the outer peripheral surface of the cylindrical body,
A sealing member surrounding the outer peripheral surface of the cylindrical body,
With
When the outer peripheral surface of the cylindrical body is surrounded by the seal member, a flow rate of a pressurized fluid flowing between the port and the cylinder chamber is controlled by the cutout groove. 2. The cylinder with a speed control mechanism according to claim 1, wherein the first notch groove and / or the second notch groove is formed such that the depth of the groove gradually increases from the piston rod toward the piston. A cylinder with a speed control mechanism, characterized in that: The cylinder with a speed control mechanism according to claim 1,
The first notch groove and / or the second notch groove may be formed such that the depth of the groove gradually increases toward a central portion along the axial direction of the cylindrical body and / or the shaft member. Cylinder with speed control mechanism. The cylinder with a speed control mechanism according to claim 1,
The said 1st notch groove and / or 2nd notch groove are the cylinders with a speed control mechanism characterized by the groove | channel of several different depths being formed in multiple steps. 4. The speed control mechanism according to claim 2, wherein the depth of the notch groove is formed so as to gradually increase from the piston rod toward the piston. With cylinder. The cylinder with a speed control mechanism according to claim 2 or 3,
The notch groove is formed so that the depth of the groove gradually increases toward a central portion along the axial direction of the cylindrical body and / or the shaft member. The cylinder with a speed control mechanism according to claim 2 or 3,
The cylinder with a speed control mechanism, wherein the notch groove is formed in a multi-stage shape having a plurality of different groove depths.

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