This application is based upon and claims the benefit of priority from prior Japanese Patent Application No. 2014-258964, filed on Dec. 22, 2014, the entire contents of which are incorporated herein by reference.
The present invention relates to a rotary actuator that changes, for example, a control surface of an aircraft wing.
Japanese Laid-Open Patent Publication No. 2013-113347 describes a rotary actuator that includes an output shaft, an arcuate piston, and a cylinder, which accommodates the output shaft and the piston. A seal is attached to the piston, An arcuate first pressure chamber and an arcuate second pressure chamber are defined in the cylinder. In the rotary actuator, pressure fluid is supplied to one of the first pressure chamber and the second pressure chamber and discharged from the other one of the first pressure chamber and the second pressure chamber to push the piston and rotate the output shaft. The arcuate-piston-type rotary actuator reduces the leakage of the pressure fluid as compared to a vane-type rotary actuator.
In the rotary actuator described in Japanese Laid-Open Patent Publication No. 2013-113347, an arm connects the piston to the output shaft. When the pressure fluid pushes the piston, the piston is pressed against the inner circumferential surface of the cylinder about a portion where the piston and the arm are connected. This increases the friction between the piston and the cylinder and decreases the ratio of the drive torque of the output shaft relative to the force of the pressure fluid pushing the pistons. That is, the output efficiency of the rotary actuator is lowered.
It is an object of the present invention to provide a rotary actuator in which a piston is smoothly movable relative to a cylinder.
One aspect of the present invention is a rotary actuator that includes an output shaft, a housing, at least one piston, and a friction reducer. The housing includes at least one arcuate bore that extends around the output shaft. The at least one piston is coupled to the output shaft and moved in the arcuate bore. Pressure fluid acts to move the piston. The friction reducer is configured to reduce friction between a peripheral surface of the piston and an inner circumferential surface of the housing forming the arcuate bore.
In the rotary actuator, the friction reducer reduces the friction between the peripheral surface of the piston and the inner circumferential surface of the housing. Thus, even when the pressure fluid of the pressure chamber presses the peripheral surface of the piston against the inner circumferential surface of the housing, the piston is smoothly movable relative to the housing. This improves the output efficiency of the rotary actuator.
In some implementations, the friction reducer includes a roller that is in contact with the peripheral surface of the piston, and the roller rolls when the piston moves.
In the rotary actuator, the roller supports the peripheral surface of the piston. Thus, the sliding friction between a portion of the peripheral surface of the piston and the inner circumferential surface of the housing is converted into rolling friction of the roller. This reduces the friction between the peripheral surface of the piston and the inner circumferential surface of the housing and allows the piston to smoothly move relative to the housing.
In some implementations, the roller is supported by a bearing.
In the rotary actuator, the bearing further easily rolls the roller. This reduces the rolling friction of the piston and the roller.
In some implementations, the peripheral surface of the piston includes an arcuate outer surface, and the roller is in linear contact with the arcuate outer surface.
In the rotary actuator, the roller is resistant to deformation compared to a structure in which the peripheral surface of the piston is in point contact with the roller. This allows the roller to easily roll relative to the piston.
In some implementations, the friction reducer includes a stopper that reduces force pressing the piston against the inner circumferential surface of the housing.
In the rotary actuator, the force pressing the piston against the inner circumferential surface of the housing is decreased compared to a structure that does not include a stopper. This limits increases in the friction between the peripheral surface of the piston and the inner circumferential surface of the housing.
In some implementations, the output shaft includes an arm coupled to the piston, the piston and the arm are coupled in an axial direction of the output shaft by a first coupling portion and a second coupling portion, the first coupling portion and the second coupling portion are separated from each other, and at least one of the first coupling portion and the second coupling portion configures the stopper.
In the rotary actuator, the coupling portion of the arm and the piston configure a stopper. This simplifies the structure of the rotary actuator compared to, for example, when the stopper is a coupling rod, which couples the output shaft and the piston.
In some implementations, the rotary actuator further includes an outer fluid bearing chamber defined between the peripheral surface of the piston and the inner circumferential surface of the housing. The outer fluid bearing chamber is in communication with a pressure chamber defined by the piston and the arcuate bore. The stopper includes the outer fluid bearing chamber and a fluid passage, which communicates the pressure chamber and the outer fluid bearing chamber.
In the rotary actuator, the hydraulic pressure of the outer fluid bearing chamber is applied through the fluid passage and inwardly pushes the peripheral surface of the piston. This decreases the force pressing the peripheral surface of the piston against the inner circumferential surface of the housing. Additionally, the movement of the piston moves the outer fluid bearing chamber moves. Thus, the outer fluid bearing chamber may be formed in a desired position regardless of a movement range of the piston. This increases the degree of freedom for a location where the outer fluid bearing chamber is formed.
In some implementations, the at least one piston includes a first piston and a second piston. The first piston and the second piston are located at opposite sides of the output shaft. The stopper includes a coupling rod that couples the first piston and the second piston in a radial direction.
In the rotary actuator, the coupling rod functions as a stopper shared by the first piston and the second piston. Thus, when the rotary actuator includes a plurality of pistons, the number of components of the rotary actuator is reduced compared to a structure in which a stopper is arranged for each stopper.
In some implementations, the at least one piston includes a first piston and a second piston. The first piston and the second piston are located at opposite sides of the output shaft. The stopper includes a ring that couples the first piston and the second piston.
In the rotary actuator, the ring functions as a stopper shared by the first piston and the second piston. Thus, when the rotary actuator includes a plurality of pistons, the number of components of the rotary actuator is reduced compared to a structure in which a stopper is arranged for each stopper.
In some implementations, the piston includes a head and a non-head portion, and the friction reducer is configured to mechanically interact with a radially outer surface of the non-head portion of the piston at a location other than the arcuate bore.
In some implementations, the roller is arranged adjacent to or separated from the arcuate bore in a circumferential direction.
Another aspect of the present invention is a rotary actuator that includes an output shaft, a housing, a piston, and a rolling bearing. The housing includes an arcuate bore that extends around the output shaft. The piston is coupled to the output shaft and moved in the arcuate bore. Pressure fluid acts to move the piston. The rolling bearing includes a rotational race and a bearing roller. The rotational race forms the arcuate bore. The rotational race is in contact with the peripheral surface of the piston. The bearing roller is located between the inner circumferential surface of the housing and the rotational race.
In the rotary actuator, when the piston moves, the rotational race of the rolling bearing rotates in the movement direction of the piston. Thus, even when the peripheral surface of the piston is pressed against the rotational race, the piston is smoothly movable.
In some implementations, the piston includes an outer side surface, and at least a portion of the outer side surface of the piston and the inner circumferential surface of the housing are spaced apart by a gap.
The inventors of the present application have found that the friction is reduced between the peripheral surface of the piston and the inner circumferential surface of the housing when decreasing the size of an area of the peripheral surface of the piston that contacts the inner circumferential surface of the housing. Hence, the rotary actuator includes a gap between the outer side surface of the piston and the inner circumferential surface of the housing. This reduces the friction and allows the piston to smoothly move relative to the housing.
Other aspects and advantages of the invention will become apparent from the following description, taken in conjunction with the accompanying drawings, illustrating by way of example the principles of the invention.
The invention, together with objects and advantages thereof, may best be understood by reference to the following description of the presently preferred embodiments together with the accompanying drawings in which:
The structure of a first embodiment of a rotary actuator 1 will now be described with reference to
Referring to
The rotary actuator 1 includes a case 10, which includes a tubular case body 11 having two opposite open ends. A tubular or annular block 12 is fixed to each of the two opposite ends of the case body 11 to close the opening of the case body 11. The case 10 includes an inner cavity, which is surrounded by the case body 11 and the two blocks 12. The inner cavity accommodates a cylinder 20, which is one example of a housing, and the output shaft 40. The dashed line of
The cylinder 20 includes five cylinder blocks 30, which are stacked in the axial direction. As shown in
The inner cavity 21 of the cylinder 20 includes a plurality of arcuate bores 22 and open regions 23. Each arcuate bore 22 is formed between axially adjacent ones of the cylinder blocks 30. The open regions 23 in the five cylinder blocks 30, which are stacked in the axial direction, form voids extending through the cylinder 20.
Here, the number of the arm units 50 and the number of the pistons are not limited. For example, one piston may be used. Alternatively, three or more pistons may be included in each piston set. The number of the cylinder blocks 30 may be changed in accordance with the number of the arm units 50 and the pistons.
As shown in
Each arcuate bore 22 is encompassed by the corresponding inner wall 34, the portion of the outer wall 31 opposed to the inner wall 34, and the corresponding bottom wall 32. The arcuate bore 22 is an elongated hole that is arcuate about the output shaft 40. More specifically, the arcuate bores 22 are located in two radially opposed portions of the cylinder 20 (refer to
As shown in
The piston 60A is coupled to a distal portion of the corresponding arm pair 51A. The piston 60B is coupled to a distal portion of the corresponding arm pair 51B. The piston 60A includes an arcuate piston body 61 and an arcuate piston head 62 (also referred to as seal portion), which is located on the distal end of the piston body 61. The arcuate piston body 61 may be referred to as a non-head portion of the piston.
The seal portion 62 of the piston 60A has a circular end surface 62A. An annular packing 63 is coupled to the seal portion 62. One example of the packing 63 is an O-ring.
A coupling hole 61B extends through a basal portion of the piston body 61 in the axial direction and receives a bolt 70. When the basal portion of the piston body 61 is located between the two arms 52 of the arm pair 51A, the piston body 61 is pivotally coupled to the arm pair 51A by the bolt 70 and a nut 71. Instead of having the arcuate shape, the piston body 61 may, for example, be shaped straight and extend toward the arms 52.
The peripheral surface of the arcuate piston body 61 of the piston 60A includes an arcuate outer side surface 61A, which is parallel to the axis Ax. As shown in
As shown in
The two rolling bearings 82 are coupled to two axial ends of the roller 81. The rolling bearings 82 are coupled to the bearing supports 32B of the cylinder block 30. Thus, the rolling bearings 82 are located at axially opposite sides of the piston body 61.
As shown in
As shown in
As shown in
The structure of a driver 90 including the rotary actuator 1 will now be described with reference to
The driver 90 includes a hydraulic pressure source 91, which supplies the hydraulic oil to the rotary actuator 1, and a reservoir 92, to which the hydraulic oil is discharged from the rotary actuator 1. A control valve 93, which switches the supply-discharge mode of the hydraulic oil of the rotary actuator 1, is located between the hydraulic pressure source 91 and the reservoir 92. The operations of the control valve 93 and the hydraulic pressure source 91 are controlled, for example, by a controller 94 including a microcomputer. The hydraulic pressure source 91, the reservoir 92, the control valve 93, and the rotary actuator 1 are connected by oil passages.
The control valve 93 is, for example, a solenoid valve and connected to the hydraulic pressure source 91, the reservoir 92, and the rotary actuator 1. The control valve 93 may be shifted to a first communication position 93X, a second communication position 93Y, and an interruption position 931. In the first communication position 93X, the control valve 93 supplies hydraulic oil from the hydraulic pressure source 91 to the first hydraulic chambers 37A, 37B and discharges hydraulic oil from the second hydraulic chambers 38. In the second communication position 93Y, the control valve 93 supplies hydraulic oil from the hydraulic pressure source 91 to the second hydraulic chambers 38 and discharges hydraulic oil from the first hydraulic chambers 37A, 37B. In the interruption position 93Z, the control valve 94 interrupts the supply of hydraulic oil from the hydraulic pressure source 91 to the rotary actuator 1 and interrupts the discharge of hydraulic oil from the rotary actuator 1 to the reservoir 92.
The operation of the rotary actuator 1, which is driven by the driver 90, will now be described.
When forwardly rotating the output shaft 40, the controller 94 controls and shifts the control valve 93 to the first communication position 93X. Thus, hydraulic oil is supplied from the hydraulic pressure source 91 to the first hydraulic chambers 37A, 37B and discharged from the second hydraulic chambers 38. Consequently, the pistons 60A, 60B orbit in the forward direction (clockwise direction in
When reversely rotating the output shaft 40, the controller 94 controls and shifts the control valve 93 to the second communication position 93Y. Thus, hydraulic oil is supplied from the hydraulic pressure source 91 to the second hydraulic chambers 38 and discharged from the first hydraulic chambers 37A, 37B. Consequently, the pistons 60A, 60B orbit in the reverse direction (counterclockwise direction in
Additionally, when stopping the rotation of the output shaft 40, the controller 94 controls and shifts the control valve 93 to the interruption position 93Z. This interrupts the supply and discharge of the hydraulic oil of the first hydraulic chambers 37A, 37B and the second hydraulic chambers 38. Thus, the pistons 60A, 60B do not orbit. This stops the rotation of the output shaft 40.
The first embodiment has the effects and advantages described below.
(1) When hydraulic oil is supplied to, for example, the first hydraulic chambers 37A, 37B, hydraulic pressure applied to the end surface 62A of the seal portion 62 of each of the pistons 60A, 60B acts to pivot the corresponding seal portion 62 outward in the radial direction about the bolt 70. This presses a circumferential surface 62B of each seal portion 62 against the inner circumferential surface 31C of the outer wall 31 of the cylinder block 30 so that the pistons 60A, 60B orbit in the forward direction.
The piston bodies 61 of the pistons 60A, 60B are supported by the rollers 81, which function as the friction reducers 80. Thus, the forward orbiting of the pistons 60A, 60B rotates the rollers 81. When the pistons 60A, 60B orbit in the forward direction, the seal portions 62 is a sliding friction and the piston bodies 61 are rolling frictions.
Thus, the friction between each piston body 61 and the inner circumferential surface 31C of the outer wall 31 is smaller than when the friction between the inner circumferential surface 31C of the outer wall 31 and each of the seal portions 62 and the piston bodies 61 is a sliding friction.
Additionally, the rollers 81 support the piston bodies 61 at an inner side of the inner circumferential surface 31C of the outer wall 31. This decreases the force pressing the circumferential surface 62B of each seal portion 62 against the inner circumferential surface 31C of the outer wall 31. Thus, friction is reduced between the circumferential surface 62B of each seal portion 62 and the inner circumferential surface 31C of the outer wall 31. The reduction in friction between the circumferential surface 62B of the seal portion 62 in each of the pistons 60A, 60B and the inner circumferential surface 31C of the outer wall 31 results in smooth movement of the pistons 60A, 60B. This improves the output efficiency of the rotary actuator 1.
(2) Each friction reducer 80 includes the rolling bearings 82, which support the roller 81 so that the roller 81 is rotatable relative to the cylinder block 30. This facilitates the rolling of the rollers 81 when the pistons 60A, 60B orbit and reduces the rolling friction between the pistons 60A, 60B and the rollers 81.
(3) Each roller 81 is in linear contact with the arcuate outer side surface 61A of the piston body 61 of the corresponding one of the pistons 60A, 60B. Thus, the roller 81 is more resistant to deformation than a structure in which the roller 81 is in point contact with the peripheral surface of the piston body 61 of the corresponding one of the pistons 60A, 60B. This allows the rollers 81 to easily roll relative to the pistons 60A, 60B.
(4) The inventors of the present application have found that the friction is reduced between the pistons 60A, 60B and the outer wall 31 when the piston bodies 61 of the pistons 60A, 60B do not contact the inner circumferential surface 31C of the outer wall 31 of the cylinder block 30. If the piston bodies 61 are configured to contact the inner circumferential surface 31C of the outer wall 31 when the pistons 60A, 60B orbit and the pistons 60A, 60B receive the hydraulic pressure of the first hydraulic chambers 37A, 37B, the piston bodies 61 deform outward in the radial direction and press the inner circumferential surface 31C of the outer wall 31. This increases the friction between the piston bodies 61 and the inner circumferential surface 31C of the outer wall 31. However, if the piston bodies 61 of the pistons 60A, 60B are not in contact with the inner circumferential surface 31C of the outer wall 31, the piston bodies 61 do not press the inner circumferential surface 31C of the outer wall 31 even when deformed. Thus, it is understood that friction is reduced between the pistons 60A, 60B and the inner circumferential surface 31C of the outer wall 31.
In this regard, in the present embodiment, the gap G is formed between the piston bodies 61 of the pistons 60A, 60B and the inner circumferential surface 31C of the outer wall 31 so that even when deformed outward in the radial direction, the piston bodies 61 do not contact the inner circumferential surface 31C of the outer wall 31. This decreases the area of the pistons 60A, 60B contacting the inner circumferential surface 31C of the outer wall 31 and allows the pistons 60A, 60B to smoothly move.
(5) The bearing supports 32B of each cylinder block 30 are formed in the axial ends of the cylinder block 30. This increases the axial distance between the two rolling bearings 82, which support the roller 81. Thus, the inclination of the roller 81 is decreased when the two bearing supports 32B are misaligned due to machining errors of the cylinder block 30 and assembling errors of the cylinder 20. This limits the force of the rollers 81 that press the pistons 60A, 60B and limits increases in the friction between the rollers 81 and the arcuate outer side surfaces 61A of the pistons 60A, 60B.
The structure of a second embodiment of the rotary actuator 1 will now be described with reference to
As shown in
A piston 110A includes an arcuate piston body 111 and a seal portion 115, which extends from a distal portion of the piston body 111 in the circumferential direction. The seal portion 115 includes a circular end surface. An annular packing 116 is attached to the seal portion 115. One example of the packing 116 is an O-ring. The piston body 111 is overlapped with the second arm 103 in the axial direction. A portion of the piston body 111 that is overlapped with the second arm 103 is cut away in the axial direction to form a cutaway portion 112. A first fastening hole 113 and a second fastening hole 114 are formed in parts of the cutaway portion 112 that are opposed to the first insertion hole 104 and the second insertion hole 105, respectively. A piston 110B has the same form as the piston 110A.
A first bolt 121 is inserted through the first insertion hole 104 and fastened to the first fastening hole 113, and a second bolt 122 is inserted through the second insertion hole 105 and fastened to the second fastening hole 114. This fastens the arm 101A and the piston 110A to each other. The counterbore 104A accommodates a bolt head of the first bolt 121, and the counterbore 105A accommodates a bolt head of the second bolt 122 (refer to
The first insertion hole 104, the first fastening hole 113, and the first bolt 121 configure a first coupling portion and a stopper. The second insertion hole 105, the second fastening hole 114, and the second bolt 122 configure a second coupling portion and a stopper.
The arm 101A and the piston 110A may be coupled at three or more locations. Also, the arm 101B and the piston 110B may be coupled at three or more locations. Alternatively, the arm 101A and the piston 110A may be formed by a single member. Also, the arm 101B and the piston 110B may be formed by a single member. When the arm 101A and the piston 110A are formed by a single member and the arm 101E and the piston 110E are formed by a single member, the insertion holes 104, 105, the fastening holes 113, 114, and the bolts 121, 122 are omitted.
The second embodiment has the effects and advantages described below.
As shown in
Additionally, the structure of the rotary actuator 1 is simplified compared to a structure additionally including a coupling rod that couples the output shaft 40 and the pistons 110A, 110B and functions as a stopper restricting the radially outward movement of the seal portions 115 of the pistons 110A, 110B.
The structure of a third embodiment of the rotary actuator 1 will now be described with reference to
As shown in
The pistons 60A, 60B each include an oil inlet 66, which is one example of a stopper and a fluid passage that communicates the end surface 62A of the seal portion 62 and a portion in the peripheral surface of the piston body 61 surrounded by the annular groove 64. Each oil inlet 66 includes a first oil passage 66A, which extends straight in a direction orthogonal to the end surface 62A, and a second oil passage 66B, which radially extends from the first oil passage 66A. The first oil passage 66A has a larger cross-sectional area than the second oil passage 66B.
As shown in
Each outer hydraulic chamber 39 may be formed in a portion of the piston body 61 that is farther from the seal portion 62 than the outer hydraulic chamber 39 of the third embodiment. Additionally, the oil inlets, which communicate the first hydraulic chambers 37A, 37B and the outer hydraulic chambers 39, may be formed in the outer wall 31 of the cylinder block 30 instead of the pistons 60A, 60B. In this case, the outer hydraulic chambers 39 are formed in the outer wall 31 so that the oil inlets and the outer hydraulic chambers 39 remain in communication even when the pistons 60A, 60B orbit.
The third embodiment has the effects and advantages described below.
(1) The outer hydraulic chambers 39, which are in communication with the first hydraulic chambers 37A, 37B through the oil inlets 66, are formed between the pistons 60A, 60B and the inner circumferential surface 31C of the outer wall 31 of the cylinder block 30. Thus, the hydraulic pressure of the first hydraulic chambers 37A, 37B is applied to the outer hydraulic chambers 39. Consequently, as shown in
(2) The packings 65, which are attached to the annular grooves 64 of the piston bodies 61, form the outer hydraulic chambers 39. Thus, when the pistons 60A, 60B move, the outer hydraulic chambers 39 move integrally with the pistons 60A, 60B. This allows the outer hydraulic chambers 39 to be formed regardless of the movement range of the pistons 60A, 60B.
(3) Each outer hydraulic chamber 39 is formed in a portion of the piston body 61 that is adjacent to the seal portion 62. Thus, the outer hydraulic chamber 39 acts to further directly support the circumferential surface 62B of the seal portion 62 that is pressed against the inner circumferential surface 31C of the outer wall 31. This further decreases the force pressing the circumferential surface 62B of the seal portion 62 against the inner circumferential surface 31C of the outer wall 31.
The structure of a fourth embodiment of the rotary actuator 1 will now be described with reference to
A through hole 41 extends through the output shaft 40 in the radial direction. The through hole 41 receives a coupling rod 130, which is one example of a stopper included in the friction reducer. The coupling rod 130 projects out of the output shaft 40 in the radial direction and is coupled to an inner side surface of each of the pistons 60A, 60B. More specifically, the coupling rod 130 couples the pistons 60A, 60B to each other. The coupling rod 130 intersects with the axis of the output shaft 40. The coupling rod 130 is coupled to a portion of each of the pistons 60A, 60B separated from the bolt 70 in the circumferential direction so that the coupling rod 130 cannot be rotated relative to the pistons 60A, 60B. In the fourth embodiment, a plurality of pistons such as the pistons 60A, 60B are necessary.
The coupling rod 130 may be rotationally coupled to the pistons 60A, 60B. In this case, the coupling rod 130 is rotationally coupled to projections (not shown), which project from the piston bodies 61 of the piston 60A, 60B in the axial direction.
The fourth embodiment has the effects and advantages described below.
(1) The pistons 60A, 60B receive force that moves the pistons 60A, 60B outward in the radial direction. The coupling rod 130, which couples the pistons 60A, 60B in the radial direction, limits increases in the radial distance between the pistons 60A, 60B. Additionally, the pistons 60A, 60B receive force that moves the pistons 60A, 60B in radially opposite directions. However, the length of the coupling rod 130 does not change. Thus, the force moving the piston 60A outward in the radial direction offsets the force moving the piston 60B outward in the radial direction. This decreases the force pressing the circumferential surfaces 62B of the seal portions 62 of the pistons 60A, 60B against the inner circumferential surface 31C of the outer wall 31 and reduces the friction between the seal portions 62 and the outer wall 31. Consequently, the smooth movement of the pistons 60A, 60B improves the output efficiency of the rotary actuator 1.
(2) The coupling rod 130 couples the pistons 60A, 60B to each other. Thus, the coupling rod 130 functions as a stopper shared by the pistons 60A, 60B. This reduces the number of components of the rotary actuator 1 compared to a structure in which each of the pistons 60A, 60B include a stopper.
The structure of a fifth embodiment of the rotary actuator 1 will now be described with reference to
A rolling bearing 140 is coupled to the inner circumferential surface 31C of the outer wall 31 of the cylinder block 30. The rolling bearing 140 includes an outer race 141, which is coupled to the inner circumferential surface 31C of the outer wall 31, an inner race 142, which is separated from the outer race 141 inward in the radial direction and is one example of a rotational race, and a plurality of bearing rollers 143, which is located between the outer race 141 and the inner race 142. The packings 63 of the seal portions 62 of the pistons 60A, 60B are in contact with an inner circumferential surface of the inner race 142. One example of the bearing roller 143 is a ball.
In the first embodiment, the arcuate bore 22 is a cavity surrounded by the inner walls 34, portions of the outer wall 31 opposed to the inner walls 34, and the bottom walls 32. Instead, the arcuate bore 22 is a cavity surrounded by portions of the inner race 142 opposed to the inner walls 34, the inner walls 34, and the bottom walls 32.
Here, the bearing roller 143 may be a roller other than a ball such as a tubular roller or a needle roller. Additionally, the outer race 141 may be omitted from the rolling bearing 140. In this case, the outer wall 31 is configured to be an outer race.
The fifth embodiment has the effects and advantages described below.
The rotary actuator 1 includes the rolling bearing 140, which is in contact with the pistons 60A, 60B. Thus, when the pistons 60A, 60B orbit, the inner race 142 of the rolling bearing 140, which is in contact with the seal portions 62, rotates integrally with the pistons 60A, 60B. Consequently, the smooth orbit of the pistons 60A, 60B improves the output efficiency of the rotary actuator 1.
It should be apparent to those skilled in the art that the present invention may be embodied in many other specific forms without departing from the scope of the invention. Particularly, it should be understood that the present invention may be embodied in the following forms.
The stopper, which reduces the force pressing the circumferential surfaces 62B, 115A of the seal portions 62, 115 of the pistons 60A, 60B, 110A, 110B against the inner circumferential surface 31C of the outer wall 31, may have a structure shown in
As shown in
As shown in
Instead of the roller 81 of the first embodiment, the friction reducer may include balls 170, which are located between the pistons 60A, 60B and the outer wall 31 as shown in
16, the balls 170 are embedded in the piston body 61 of the piston 60B.
The structure of the rollers 81, which support the pistons 60A, 60B of the first embodiment, may be changed to those shown in
As shown in
As shown in
In the first embodiment, the rollers 81 are located at radially outer sides of the pistons 60A, 60B. Instead, the rollers 81 may be located in radially middle portions of the pistons 60A, 60B. More specifically, arcuate through holes extend through the radially middle portions of the pistons 60A, 60B in the axial direction. The rollers 81 are inserted into the through holes. When the pistons 60A, 60B orbit, the rollers 81 roll relative to the pistons 60A, 60B in contact with the walls of the through holes. This obtains advantage (1) of the first embodiment.
The arcuate outer side surface 61A may be omitted from the piston body 61 of each of the pistons 60A, 60B of the first embodiment. In this case, the piston body 61 is formed in the same manner as the seal portion 62. Additionally, the roller 81 is in point contact with the piston body 61. Further, when the arcuate outer side surface 61A is omitted from the piston body 61, the piston body 61 may be formed so that the peripheral surface of the piston body 61 contacts the inner circumferential surface 31C of the outer wall 31.
In the second embodiment, the coupling structure of the pistons 110A, 110B and the arms 101A, 101B is not limited to such a structure in which the first bolt 121 and the second bolt 122 are respectively fastened to the first fastening hole 113 and the second fastening hole 114.
In one example, at least one of the first fastening hole 113 and the second fastening hole 114 may be changed to an insertion hole, which is capable of receiving the corresponding one of the first bolt 121 and the second bolt 122. In this structure, when the insertion hole receives the corresponding one of the first bolt 121 and the second bolt 122, a nut may be coupled to the inserted bolt. In this case, the insertion hole and the inserted bolt form no gap or a slight gap. Thus, the insertion hole and the inserted bolt function as a stopper, which decreases the force pressing the circumferential surfaces 62B of the seal portions 62 against the inner circumferential surface 31C of the outer wall 31 of the cylinder block 30.
In another example, one of the first bolt 121 and the second bolt 122 may be omitted. In this case, the pistons 110A, 110B each include a projection, and the arms 101A, 101B each include a recess. Alternatively, the pistons 110A, 110B can each include a recess, and the arms 101A, 101B can each include a projection. In this case, the projection and recess function as a stopper and a coupling portion of each of the pistons 110A, 110B and the arms 101A, 101B.
In another example, when the arms 101A, 101B are configured to be axially extended and circumferentially opposed to the pistons 110A, 110B, and the cutaway portions 112 are omitted from the pistons 110A, 110B, the arms 101A, 101B and the pistons 110A, 110B may be configured to be fixed in the circumferential direction. In one example of the structure for fixing the arms 101A, 101B and the pistons 110A, 110B in the circumferential direction, the arms 101A, 101B each include a circumferential end projection, and the pistons 110A, 110B each include a circumferential end press-fitting hole, to which the projection is press-fitted. Alternatively, the pistons 110A, 110E can each include a circumferential end projection, and the arms 101A, 101B can each include a circumferential end press-fitting hole, to which the projection is press-fitted.
In the first and third to fifth embodiments, the rotary actuator 1 has a structure in which the pistons 60A, 60B are fastened to the arm pairs 51A, 51B by the bolts 70 and the nuts 71 when located between the two arms 52 of the arm pairs 51A, 51B. The coupling structure of the arm pairs 51A, 51B and the pistons 60A, 60B is not limited to such a structure. For example, instead of the bolts 70 and the nuts 71, as shown in
In the rotary actuator 1 of the third and fourth embodiments, when the hydraulic pressure of the first hydraulic chambers 37A, 37B pushes the pistons 60A, 60B, the piston bodies 61, 111 of the pistons 60A, 60B, 110A, 110B contact the inner circumferential surface 31C of the outer wall 31. Instead, in the same manner as the first embodiment, the rotary actuator 1 of the third and fourth embodiments may include the gap G between the piston bodies 61, 111 and the inner circumferential surface 31C of the outer wall 31 so that the piston bodies 61, 111 of the pistons 60A, 60B, 110A, 110B do not contact the inner circumferential surface 31C of the outer wall 31.
The above description is intended to be illustrative, and not restrictive. For example, the above-described examples (or one or more aspects thereof) may be used in combination with each other. Other embodiments can be used, such as by one of ordinary skill in the art upon reviewing the above description. Also, in the above detailed description, various features may be grouped together to streamline the disclosure. This should not be interpreted as intending that an unclaimed disclosed feature is essential to any claim. Rather, inventive subject matter may lie in less than all features of a particular disclosed embodiment. Thus, the following claims are hereby incorporated into the detailed description, with each claim standing on its own as a separate embodiment. The scope of the invention should be determined with reference to the appended claims, along with the full scope of equivalents to which such claims are entitled.
Number | Date | Country | Kind |
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2014-258964 | Dec 2014 | JP | national |