JP6625867B2 - Hydraulic equipment - Google Patents

Description

  BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a hydraulic device in which two hydraulic mechanism units each having a pair of gears whose teeth mesh with each other are arranged side by side in the axial direction.

  Into the hydraulic device provided with the pair of gears, a gear pump is appropriately rotated by a drive motor, and a hydraulic pump that pressurizes and discharges the working liquid by the rotating operation of the gear and a working liquid that is pressurized in advance is introduced. Hydraulic motors that rotate the gears and use the rotational force of the rotating shaft as power.

  Conventionally, there has been known a hydraulic device in which a first hydraulic mechanism and a second hydraulic mechanism each having a pair of gears are arranged side by side in the axial direction, that is, continuously. In this hydraulic device, for example, when this is a hydraulic pump, the first hydraulic mechanism is configured so that the working liquid discharged from the hydraulic pump has a high pressure, and the second hydraulic mechanism is Is configured such that the pressure of the working liquid discharged from it becomes lower than the pressure of the working liquid discharged from the first hydraulic mechanism. Then, according to the required pressure of the working liquid, for example, when high-pressure working liquid is required, only the first hydraulic mechanism is driven, and when low-pressure working liquid is required, The first hydraulic mechanism and the second hydraulic mechanism are selectively used according to the required pressure of the working liquid such that only the second hydraulic mechanism is driven.

  By the way, a variety of shapes are conventionally used as the pair of gears, and among them, there is a hydraulic device using a helical gear. Although the helical gear has a structure in which the teeth are obliquely inclined, the tooth contact of the gear is dispersed, so that it has a characteristic that noise is small, but on the other hand, it is used as a hydraulic device. In this case, there is a characteristic that an axial thrust force (engagement thrust force) is generated by the meshing of the teeth, and a thrust force (pressure receiving thrust force) is similarly generated by receiving the pressure of the working liquid on the tooth surface.

  The thrust force periodically fluctuates due to the rotation of the gear, and the periodic fluctuation causes the gear and the bearing member to vibrate to generate noise, or the vibration causes the end face of the gear and the end face of the bearing member to vibrate. Between the high-pressure side and the low-pressure side through the gap.

  Therefore, in order to solve such a problem, a force (drag force) in a direction opposite to the thrust force is applied to the rotating shaft of the gear so as to suppress the axial displacement of the gear. A hydraulic pump has been proposed (see Patent Document 1 below).

  This hydraulic pump device is configured by juxtaposing first and second hydraulic mechanisms having a pair of helical gears. The first hydraulic mechanism has a first helical gear having a first rotating shaft, and a second helical gear having a second rotating shaft and meshing with the first helical gear. A first main body having a first hydraulic chamber in which both end portions are open and in which the first and second helical gears are housed in a meshing state; First and second bearing members rotatably supporting a second rotating shaft, wherein the first hydraulic chamber is configured such that one of the first hydraulic chambers is on a low pressure side with respect to a meshing portion of the first and second helical gears; The other is set to the high pressure side.

  The second hydraulic mechanism includes a third helical gear having a third rotating shaft, and a fourth helical gear having a fourth rotating shaft and meshing with the third helical gear. A second main body having a second hydraulic chamber in which both end portions are open and in which the third and fourth helical gears are housed in a meshed state; Third and fourth bearing members rotatably supporting a fourth rotating shaft, wherein one of the second hydraulic chambers has a low pressure side with respect to a meshing portion of the third and fourth helical gears. , The other is set to the high pressure side.

  In addition, the first and second hydraulic mechanisms are juxtaposed so that the first rotation axis and the third rotation axis are located coaxially, and are provided between the first main body and the second main body. Is provided with an intermediate plate (more specifically, composed of first and second intermediate plates), and the first and second main bodies are fixed to the intermediate plate, The front opening, which is the other opening of the main body, is sealed with a front plate, and the rear opening, which is the other opening of the second main body, is sealed with a rear plate.

  Also, a front shaft portion of the first rotation shaft extends to the outside through the front plate, and a rear shaft end of the first rotation shaft and a front shaft of the third rotation shaft. The ends are respectively inserted into through holes formed in the intermediate plate, and are connected so as to rotate integrally by a coupling formed with a spline.

  Further, in the first hydraulic mechanism, a combined force of a thrust force caused by engagement of the first and second helical gears and a thrust force caused by the high-pressure side working fluid is applied to the first rotation shaft and the second rotation shaft. And the second hydraulic mechanism is configured such that the combined force of the thrust force due to the meshing of the third and fourth helical gears and the thrust force due to the working liquid on the high-pressure side of the second hydraulic mechanism is equal to the third force. It is configured to act rearward on the third rotation axis and the fourth rotation axis.

  In the rear plate, cylinder holes serving as cylinder chambers are formed in portions facing the respective rear end surfaces of the third rotation shaft and the fourth rotation shaft, and a third rotation shaft is formed in each cylinder hole. A piston is inserted so as to be able to abut each rear end surface of the fourth rotary shaft, and further, a flow path communicating with a cylinder chamber of each of the cylinder holes and a high pressure side of the second hydraulic chamber is formed. By supplying the working fluid on the high pressure side of the second hydraulic chamber to each cylinder chamber, each of the pistons is urged forward, and each of the pistons causes the third rotation axis and the fourth rotation axis to move forward. Pressed.

  A stepped compensation ring having a large-diameter portion on the front side and a small-diameter portion on the rear side is externally fitted to the rear end of the first rotating shaft, and the intermediate plate is provided with two seals. A hydraulic chamber for urging is formed on the rear end surface (back surface) of the large diameter portion, and a flow path communicating with the hydraulic chamber for urging and the high pressure side of the first hydraulic chamber is formed. When the working fluid on the high pressure side of the first hydraulic chamber is supplied to the back surface of the large diameter portion, the compensation ring is urged forward, and the first rotation shaft is pressed forward by the compensation ring. It is supposed to be.

  The intermediate plate is formed with a cylinder hole serving as a cylinder chamber at a portion facing the rear end surface of the second rotation shaft, and can contact the rear end surface of the second rotation shaft with the cylinder hole. A piston is inserted into the cylinder hole, and further, a flow passage communicating with the cylinder chamber of the cylinder hole and the high pressure side of the first hydraulic pressure chamber is formed. By being supplied to the chamber, the piston is urged forward, and the second rotating shaft is pressed forward by the piston.

  Thus, according to this hydraulic pump, when the first rotating shaft is driven by an electric motor or the like, the first helical gear and the second helical gear meshing therewith rotate by this, and Rotational power is transmitted to the third rotating shaft connected thereto via the first rotating shaft, and the third helical gear and the fourth helical gear meshing therewith rotate. When the working liquid is supplied to a space set on the low pressure side of the first hydraulic chamber of the first hydraulic mechanism, the working liquid is supplied to the first helical gear and the second helical gear. It is pressurized to a high pressure by the action and discharged from the high pressure side to the outside.

  At this time, the combined force of the thrust force due to the meshing of the first and second helical gears and the thrust force due to the working liquid on the high pressure side acts rearward on the first rotation shaft and the second rotation shaft, respectively. However, the high-pressure working liquid in the first hydraulic chamber is supplied to the back of the compensation ring externally fitted to the rear end of the first rotation shaft, and the first rotation shaft is pressed forward by the compensation ring. Further, the high-pressure working liquid in the first hydraulic chamber is supplied to the cylinder chamber formed in the intermediate plate, and the second rotary shaft is pressed forward by the piston inserted therein. The thrust force acting on the first rotating shaft is reduced by the pressing force of the compensation ring, and the thrust force acting on the second rotating shaft is reduced by the pressing force of the piston.

  On the other hand, in a state where the first and second helical gears and the third and fourth helical gears are rotated, a space set on the low pressure side of the second hydraulic chamber of the second hydraulic mechanism. , The working liquid is pressurized to a high pressure by the action of the third helical gear and the fourth helical gear and discharged from the high pressure side to the outside.

  At this time, the combined force of the thrust force due to the engagement of the third and fourth helical gears and the thrust force due to the working fluid on the high pressure side acts rearward on the third and fourth rotating shafts, respectively. However, the high-pressure working liquid in the second hydraulic chamber is supplied to each of the cylinder holes formed in the rear plate, and the third and fourth rotation shafts and the fourth rotation are respectively supplied by the pistons inserted into the respective cylinder holes. The shaft is pressed forward, and each pressing force reduces the thrust force acting on the third rotating shaft and the thrust force acting on the fourth rotating shaft.

  As described above, according to this hydraulic pump, when each of the first hydraulic mechanism and the second hydraulic mechanism is used, the first rotary shaft and the second rotary shaft, and the third rotary shaft and the third rotary shaft are used. The thrust force acting on each of the four rotation shafts is acted on by a drag force to reduce the thrust force, so that the above-described problems of vibration and leakage can be suppressed. Can be.

International Publication No. 2014/191253

  However, in the above-described conventional hydraulic pump, two seals for forming a hydraulic chamber for biasing and a pressing force are applied as a structure for applying a resistance to a thrust force to the first rotating shaft. Although a structure with a compensation ring is adopted, such a structure is complicated and has a large number of parts, so that there is a problem that manufacturing costs including processing costs and assembly costs are high, and also, there is a problem that parts replacement is required. At the time of maintenance, etc., there is a problem that it takes time to disassemble and reassemble.

  Further, as described above, in the first hydraulic mechanism, a hydraulic chamber for urging the high-pressure working liquid to act on the back surface of the compensation ring is formed by two seals. Has a structure that rotates with the first rotating shaft, that is, the compensation ring and the two seals are in sliding contact with each other, and the seals provide resistance to rotation. It was not suitable.

  The present invention has been made in view of the above circumstances, and is a hydraulic device in which two hydraulic mechanisms having a pair of helical gears are arranged in parallel in the axial direction. It is an object of the present invention to provide a hydraulic device which is inexpensive, easy to maintain, and can withstand use at high speed rotation.

  The present invention for solving the above problems relates to a hydraulic device in which a first hydraulic mechanism and a second hydraulic mechanism are juxtaposed. The first hydraulic mechanism has a first helical gear having a first rotating shaft, and a second helical gear having a second rotating shaft and meshing with the first helical gear. A first main body having a first hydraulic chamber in which both end portions are open and in which the first and second helical gears are housed in a meshing state; First and second bearing members rotatably supporting a second rotating shaft, one of the first hydraulic chambers being on a low pressure side with respect to a meshing portion of the first and second helical gears. , The other is set to the high pressure side.

  The second hydraulic mechanism includes a third helical gear having a third rotating shaft, and a fourth helical gear having a fourth rotating shaft and meshing with the third helical gear. A second main body having a second hydraulic chamber in which both end portions are open and in which the third and fourth helical gears are housed in a meshed state; Third and fourth bearing members rotatably supporting a fourth rotating shaft, wherein one of the second hydraulic chambers has a low pressure side with respect to a meshing portion of the third and fourth helical gears. , The other is set to the high pressure side.

  In addition, the first and second hydraulic mechanisms are arranged side by side so that at least the first rotation axis and the third rotation axis are located coaxially, and between the first body and the second body. Is provided with an intermediate plate, the first and second main bodies are fixed to the intermediate plate, and the other opening of the first main body, which is the front opening, is sealed by the front plate, The rear opening, which is the other opening of the second body, is sealed by a rear plate.

The front shaft portion of the first rotation shaft extends through the front plate to the outside, and the rear shaft end portion of the first rotation shaft and the front shaft portion of the third rotation shaft. The shaft ends are respectively inserted into the through holes formed in the intermediate plate, are integrally rotated, and are interconnected so that the movement in the axial direction is also integrated,
In the first hydraulic mechanism, a combined force of a thrust force caused by the engagement of the first and second helical gears and a thrust force caused by the high-pressure side working liquid acts rearward on the first rotating shaft. At the same time, in the second hydraulic mechanism, the combined force of the thrust force due to the meshing of the third and fourth helical gears and the thrust force due to the working fluid on the high pressure side is directed backward with respect to the third rotating shaft. It is configured to work.

In the rear plate, a stepped first cylinder hole having a large-diameter cylinder chamber on the front side and a small-diameter cylinder chamber on the rear side is formed in a portion facing the rear end face of the third rotating shaft. A stepped first piston having a large diameter on the front side and a small diameter on the rear side is fitted into the first cylinder hole so that the front end surface thereof can abut on the rear end surface of the third rotary shaft. Inserted,
Further, a first flow path communicating with the high-pressure side of the first hydraulic chamber and one of the large-diameter cylinder chamber and the small-diameter cylinder chamber of the first cylinder hole is formed, and the high-pressure side of the second hydraulic chamber is formed. And a second flow path communicating with the other of the large-diameter cylinder chamber and the small-diameter cylinder chamber of the first cylinder hole.

  According to this hydraulic device, for example, when this is a hydraulic pump, when the first rotating shaft is driven by an electric motor or the like, this causes the first helical gear and the second helical gear meshing with the first helical gear to rotate. Rotates, and this rotational power is transmitted to the third rotating shaft connected thereto via the first rotating shaft, and the third helical gear and the fourth helical gear meshing therewith rotate. .

  For example, when the working liquid is supplied to a space set on the low pressure side of the first hydraulic chamber of the first hydraulic mechanism, the working liquid is supplied to the first helical gear and the second helical gear. It is pressurized to a high pressure by the action of the gear and discharged from the high pressure side to the outside.

  At this time, in the first hydraulic mechanism, the combined force of the thrust force due to the engagement of the first and second helical gears and the thrust force due to the working fluid on the high pressure side is directed rearward with respect to the first rotation shaft. The high-pressure hydraulic fluid in the first hydraulic chamber is supplied through the first flow path to one of the large-diameter cylinder chamber and the small-diameter cylinder chamber of the first cylinder hole formed in the rear plate. Thereby, the first piston is urged toward the front side, and the third rotating shaft is pressed forward by the first piston. Then, the pressing force of the first piston is transmitted to the first rotating shaft that is integrally connected to the third rotating shaft in the axial direction via the third rotating shaft, and acts on the first rotating shaft. The thrust force is reduced by the pressing force of the first piston.

  On the other hand, similarly, the first and second helical gears and the third and fourth helical gears are set on the low-pressure side of the second hydraulic chamber of the second hydraulic mechanism in a state where they rotate. When the working liquid is supplied to the space, the working liquid is pressurized to a high pressure by the action of the third helical gear and the fourth helical gear, and is discharged from the high pressure side to the outside.

  Then, at this time, the combined force of the thrust force due to the engagement of the third and fourth helical gears and the thrust force due to the working fluid on the high pressure side acts rearward on the third rotating shaft. The high-pressure working liquid of the second hydraulic chamber is supplied to the other of the large-diameter cylinder chamber and the small-diameter cylinder chamber of the first cylinder hole formed in the rear plate through the second flow path, whereby the One piston is urged forward, and the third piston is pressed forward by the first piston. The thrust force acting on the third rotating shaft is reduced by the pressing force of the first piston.

  Thus, according to this hydraulic device, when each of the first hydraulic mechanism and the second hydraulic mechanism is used, it acts on the first rotary shaft and the third rotary shaft respectively. The first piston acts on the thrust force to reduce the thrust force, so that the vibration problem and the leak problem described above can be suppressed.

  Further, a mechanism for imparting a drag to the first and third rotating shafts includes a stepped first cylinder hole formed in the rear plate, a first piston inserted into the first cylinder hole, and a first hydraulic pressure. A first flow path communicating between the high-pressure side of the chamber and one of the large-diameter cylinder chamber and the small-diameter cylinder chamber of the first cylinder hole, and the high-pressure side of the second hydraulic chamber and the large-diameter cylinder chamber of the first cylinder hole And the second flow path communicating with the other of the small-diameter cylinder chambers, the structure is simpler and the number of parts is smaller than that of the above-described mechanism using the conventional compensation ring, so that the processing cost and Manufacturing costs including assembly costs can be reduced.

  In addition, when performing maintenance such as replacement of parts, the hydraulic device only needs to disassemble and reassemble only the rear plate, so that maintenance can be easily performed as compared with the related art. Also, unlike the related art, since a sealing material or the like is not used to form the hydraulic chamber, the hydraulic device can be used at high speed.

  In addition, it is preferable that the drag applied to the first and third rotation shafts by the first piston is balanced with the thrust force acting on the first and third rotation shafts, respectively. As described above, the effective diameters of the large-diameter cylinder chamber and the small-diameter cylinder chamber are appropriately set according to the pressure of the working liquid on each high-pressure side of the first and second hydraulic chambers. By doing so, it is possible to more effectively prevent the above-mentioned problems of vibration and leakage from occurring.

  Further, in this hydraulic device, the first rotating shaft and the third rotating shaft may be constituted by one shaft.

Further, in the hydraulic device according to the present invention, in the first hydraulic mechanism, a combined force of a thrust force caused by the engagement of the first and second helical gears and a thrust force caused by the high-pressure side working liquid is equal to the third force. Acting rearward on the two rotating shafts, and in the second hydraulic mechanism, the combined force of the thrust force due to the meshing of the third and fourth helical gears and the thrust force due to the working liquid on the high pressure side thereof is: When acting rearward on the fourth rotation axis,
The first and second hydraulic mechanisms are arranged side by side such that the second rotation axis and the fourth rotation axis are coaxially located,
A rear shaft end of the second rotary shaft and a front shaft end of the fourth rotary shaft are respectively inserted into through holes formed in the intermediate plate, and rotate integrally with each other. It is interconnected so that movement in the axial direction is also integrated,
A stepped second cylinder hole having a large-diameter cylinder chamber on the front side and a small-diameter cylinder chamber on the rear side is formed in a portion of the rear plate facing the rear end surface of the fourth rotating shaft, A stepped second piston having a large diameter on the front side and a small diameter on the rear side is fitted into the second cylinder hole so that the front end surface thereof can be brought into contact with the rear end surface of the fourth rotary shaft,
A third flow path communicating with the high-pressure side of the first hydraulic chamber and one of the large-diameter cylinder chamber and the small-diameter cylinder chamber of the second cylinder hole is formed, and the high-pressure side of the second hydraulic chamber is connected to the third hydraulic passage. A configuration in which a fourth flow passage communicating with the other of the large-diameter cylinder chamber and the small-diameter cylinder chamber having two cylinder holes may be formed.

  According to this configuration, when the working fluid is supplied to the first hydraulic mechanism, the second cylinder hole formed in the rear plate is provided with one of a large-diameter cylinder chamber and a small-diameter cylinder chamber. The high-pressure working liquid in the first hydraulic chamber is supplied through the third flow path, whereby the second piston is urged forward, and the second piston presses the fourth rotating shaft forward. Is done. Then, the pressing force of the second piston is transmitted to the second rotating shaft integrally connected to the fourth rotating shaft in the axial direction via the fourth rotating shaft, and acts on the second rotating shaft. The thrust force is reduced by the pressing force of the second piston.

  On the other hand, when the working fluid is supplied to the second hydraulic mechanism, the second hydraulic chamber is supplied to the other of the large-diameter cylinder chamber and the small-diameter cylinder chamber of the second cylinder hole through the fourth flow path. , The second piston is urged forward, and the second piston presses the fourth rotating shaft forward. Then, the thrust force acting on the fourth rotation shaft is reduced by the pressing force of the second piston.

  Thus, according to this hydraulic device, when each of the first hydraulic mechanism and the second hydraulic mechanism is used, it acts on the second rotating shaft and the fourth rotating shaft respectively. The second piston exerts a drag against the thrust force to be applied, so that the thrust force can be reduced, and the above-described problem of vibration and leakage can be suppressed.

  Also in this case, it is preferable that the drag applied to the second and fourth rotating shafts by the second piston is balanced with the thrust force acting on the second and fourth rotating shafts, respectively. The effective diameters of the large-diameter cylinder chamber and the small-diameter cylinder chamber of the second cylinder hole are appropriately set according to the pressure of the working liquid on each high-pressure side of the first and second hydraulic chambers so that the drag becomes large. I do.

Further, in the hydraulic device according to the present invention, in the first hydraulic mechanism, a combined force of a thrust force caused by the engagement of the first and second helical gears and a thrust force caused by the high-pressure side working liquid is equal to the third force. When acting backward on the two rotation axes,
A third cylinder hole serving as a cylinder chamber is formed in a portion of the intermediate plate facing a rear end surface of the second rotation shaft, and the third cylinder hole abuts on a rear end surface of the second rotation shaft. A third piston may be inserted as much as possible, and a fifth passage may be formed to communicate between the cylinder chamber of the third cylinder hole and the high pressure side of the first hydraulic chamber.

  With this configuration, the high-pressure working liquid in the first hydraulic chamber is supplied to the cylinder chamber in the third cylinder hole through the fifth flow path, and the third piston is urged forward by the working liquid. Then, the second rotating shaft is pressed forward by the third piston. Then, the thrust force acting on the second rotating shaft is reduced by the pressing force of the third piston, whereby the problem of vibration and the problem of leakage due to the thrust force are suppressed. Also in this case, it is preferable that the drag imparted to the second rotating shaft by the third piston is in proportion to the thrust force acting on the second rotating shaft. Then, the effective diameter of the cylinder chamber of the third cylinder hole is appropriately set according to the pressure of the working liquid on the high pressure side of the first hydraulic chamber.

Further, in the hydraulic device according to the present invention, in the second hydraulic mechanism, the combined force of the thrust force due to the meshing of the third and fourth helical gears and the thrust force due to the working liquid on the high pressure side is equal to the third force. When acting rearward on the four rotation axes,
A fourth cylinder hole serving as a cylinder chamber is formed in a portion of the rear plate facing the rear end surface of the fourth rotation shaft, and the rear plate abuts on the rear end surface of the fourth rotation shaft. A fourth piston may be inserted as much as possible, and a sixth passage may be formed to communicate between the cylinder chamber of the fourth cylinder hole and the high pressure side of the second hydraulic chamber.

  With this configuration, the high-pressure working liquid in the second hydraulic chamber is supplied to the cylinder chamber in the fourth cylinder hole through the sixth flow path, and the fourth piston is urged forward by the working liquid. Then, the fourth rotation shaft is pressed forward by the fourth piston. Then, the thrust force acting on the fourth rotating shaft is reduced by the pressing force of the fourth piston, thereby suppressing the problem of vibration and the problem of leakage caused by the thrust force. Also in this case, it is preferable that the drag exerted on the fourth rotating shaft by the fourth piston is balanced with the thrust force acting on the fourth rotating shaft. Then, the effective diameter of the cylinder chamber of the fourth cylinder hole is appropriately set according to the pressure of the working liquid on the high pressure side of the second hydraulic chamber.

Further, in the hydraulic device according to the present invention, in the first hydraulic mechanism, a combined force of a thrust force caused by the engagement of the first and second helical gears and a thrust force caused by the high-pressure side working liquid is equal to the third force. When acting forward on two rotation axes,
A fifth cylinder hole serving as a cylinder chamber is formed in a portion of the front plate facing the front end surface of the second rotation shaft, and the fifth cylinder hole is in contact with the front end surface of the second rotation shaft. A fifth piston may be fitted so as to be in contact with the first hydraulic chamber, and a seventh flow path may be formed to communicate between the cylinder chamber of the fifth cylinder hole and the high pressure side of the first hydraulic chamber.

  With this configuration, the high-pressure working liquid in the first hydraulic chamber is supplied to the cylinder chamber in the fifth cylinder hole through the seventh flow path, and the fifth piston is urged rearward by the working liquid. Then, the second rotating shaft is pressed backward by the fifth piston. Then, the thrust force acting on the second rotation shaft is reduced by the pressing force of the fifth piston, thereby suppressing the problem of vibration and the problem of leakage caused by the thrust force. Also in this case, it is preferable that the drag imparted to the second rotating shaft by the fifth piston is in proportion to the thrust force acting on the second rotating shaft. Then, the effective diameter of the cylinder chamber of the fifth cylinder hole is appropriately set according to the pressure of the working liquid on the high pressure side of the first hydraulic chamber.

Further, in the hydraulic device according to the present invention, in the second hydraulic mechanism, the combined force of the thrust force due to the meshing of the third and fourth helical gears and the thrust force due to the working liquid on the high pressure side is equal to the third force. When acting forward with respect to the four rotation axes,
A sixth cylinder hole serving as a cylinder chamber is formed in a portion of the intermediate plate facing the front end surface of the fourth rotation shaft, and the sixth cylinder hole abuts on a front end surface of the fourth rotation shaft. The sixth piston may be inserted as much as possible, and an eighth flow path may be formed to communicate with the cylinder chamber of the sixth cylinder hole and the high pressure side of the second hydraulic chamber.

  With this configuration, the high-pressure working liquid in the second hydraulic chamber is supplied to the cylinder chamber in the sixth cylinder hole through the eighth flow path, and the working liquid biases the sixth piston rearward. Then, the fourth rotating shaft is pressed backward by the sixth piston. Then, the thrust force acting on the fourth rotation shaft is reduced by the pressing force of the sixth piston, thereby suppressing the problem of vibration and the problem of leakage caused by the thrust force. Also in this case, it is preferable that the drag imparted to the fourth rotating shaft by the sixth piston is in proportion to the thrust force acting on the fourth rotating shaft. Then, the effective diameter of the cylinder chamber of the sixth cylinder hole is appropriately set according to the pressure of the working liquid on the high pressure side of the second hydraulic chamber.

  As described above, according to the hydraulic device according to the present invention, when each of the first hydraulic mechanism and the second hydraulic mechanism is used, the first rotary shaft and the third rotary shaft are Since the first piston acts on the thrust force acting on each of the first and second pistons to reduce the thrust force, it is possible to suppress the above-described problems of vibration and leakage. it can.

  Further, a mechanism for imparting a drag to the first and third rotating shafts includes a stepped first cylinder hole formed in the rear plate, a first piston inserted into the first cylinder hole, and a first hydraulic pressure. A first flow path communicating between the high-pressure side of the chamber and one of the large-diameter cylinder chamber and the small-diameter cylinder chamber of the first cylinder hole, and the high-pressure side of the second hydraulic chamber and the large-diameter cylinder chamber of the first cylinder hole And the second flow path communicating with the other of the small-diameter cylinder chambers, the structure is simpler and the number of parts is smaller than that of the above-described mechanism using the conventional compensation ring, so that the processing cost and Manufacturing costs including assembly costs can be reduced.

  In addition, when performing maintenance such as replacement of parts, the hydraulic device only needs to disassemble and reassemble only the rear plate, so that maintenance can be easily performed as compared with the related art. Also, unlike the related art, since a sealing material or the like is not used to form the hydraulic chamber, the hydraulic device can be used at high speed.

FIG. 2 is a plan sectional view showing the hydraulic device according to the first embodiment of the present invention. FIG. 6 is a plan sectional view showing a hydraulic device according to a second embodiment of the present invention. It is a plane sectional view showing the hydraulic equipment concerning a 3rd embodiment of the present invention. It is a plane sectional view showing the hydraulic equipment concerning a 4th embodiment of the present invention. It is a plane sectional view showing the hydraulic equipment concerning a 5th embodiment of the present invention.

  Hereinafter, specific embodiments of the present invention will be described with reference to the drawings.

[First Embodiment]
First, a hydraulic device according to a first embodiment of the present invention will be described with reference to FIG. The hydraulic device 1 is a hydraulic pump, and includes a first hydraulic mechanism 2, a second hydraulic mechanism 15, a front plate 40, an intermediate plate 45, and a rear plate 55, as shown in FIG. Be composed.

  The first hydraulic mechanism 2 includes a first main body 7, a first helical gear 3 (hereinafter, referred to as a first gear 3), a second helical gear 5 (hereinafter, referred to as a second gear 5), It comprises a first bearing member 9 and a second bearing member 11, a first side plate 10, a second side plate 12, and the like.

  The first gear 3 has first rotating shafts 4 and 4 provided so as to extend outward from both end faces of the gear portion, and similarly, the second gear 5 has a It has the second rotating shafts 6, 6 provided so as to extend outward from both end faces. Further, the first main body 7 has a first hydraulic chamber 8 which is a space having a substantially eight-shaped cross section and a space formed with both ends opened. The first gear 3 and the second gear 5 are housed in a mutually engaged state.

  Further, the first side plate 10, the second side plate 12, the first bearing member 9, and the second bearing member 11 are members each having a substantially eight-shaped cross section, and the first side plate 10 and the second side plate 12 The first bearing member 9 and the second bearing member 11 are respectively disposed outside the first gear 3 and the second gear 5 so as to sandwich the first gear 3 and the second gear 5. The first rotating shafts 4 and 4 and the second rotating shafts 6 and 6 are rotatably supported by the second bearing member 11.

  The left side of the first main body 7 in the figure, that is, the opening on the front side is sealed by the front plate 40, and the front shaft of the first rotary shaft 4 is formed on the front plate 40. The front end 4b extends through the through hole 41 and extends outside. An electric motor (not shown) is connected to the front end 4b, and the first rotary shaft 4 is rotated. The through hole 41 is a stepped hole having a large diameter on the front side and a small diameter on the rear side, and the first rotary shaft 4 is sealed by an oil seal 42 fitted to the large diameter portion.

  The first gear 3 has a right-hand twisted tooth portion, and the second gear 5 has a left-hand twisted tooth portion. The first hydraulic chamber 8 includes the first gear 3 and the second gear 3. One is divided into a low pressure side and the other is divided into a high pressure side with a meshing portion of the gear 5 as a boundary, and the first main body 7 has an intake hole (FIG. (Not shown), and a discharge hole (not shown) communicating with the high pressure side of the first hydraulic chamber 8 is formed on the other side surface opposite to this.

  The second hydraulic mechanism 15 includes a second main body 20, a third helical gear 16 (hereinafter, referred to as a third gear 16), a fourth helical gear 18 (hereinafter, referred to as a fourth gear 18), It is composed of a third bearing member 22 and a fourth bearing member 24, a third side plate 23, a fourth side plate 25, and the like.

  The third gear 16 has third rotating shafts 17 and 17 provided to extend outward from both end faces of the gear portion, and similarly, the fourth gear 18 has a It has fourth rotating shafts 19 provided so as to extend outward from both end faces. Further, the second main body 20 has a second hydraulic chamber 21 which is a space having a substantially eight-shaped cross section and a space formed with both ends opened. The third gear 16 and the fourth gear 18 are housed in a mutually meshed state.

  The third side plate 23, the fourth side plate 25, the third bearing member 22, and the fourth bearing member 24 are members each having a substantially eight-shaped cross section, and the third side plate 23 and the fourth side plate 25 The third gear 16 and the fourth gear 18 are provided on both sides thereof so as to sandwich the third gear 16 and the fourth gear 18, and the third bearing member 22 and the fourth bearing member 24 are provided outside the third gear 16 and the fourth gear 18, respectively. The 31st rotation shafts 17, 17 and the fourth rotation shafts 19, 19 are rotatably supported by the member 22 and the fourth bearing member 24.

  The teeth of the third gear 16 are twisted to the right, the teeth of the fourth gear 18 are twisted to the left, and the second hydraulic chamber 21 is provided with the third gear 16 and the fourth gear. One end is divided into a low pressure side and the other is divided into a high pressure side with a meshing portion of the gear 18 as a boundary. The second main body 20 has an intake hole (FIG. (Not shown), and a discharge hole (not shown) communicating with the high-pressure side of the second hydraulic chamber 21 is formed on the other side surface opposite to this.

  The first hydraulic mechanism 2 and the second hydraulic mechanism 15 are arranged such that the first rotating shaft 4 and the third rotating shaft 17 are coaxially located, and the second rotating shaft 6 and the fourth rotating shaft 19 are arranged side by side so as to be coaxial with each other, and an intermediate plate 45 is disposed between mutually facing openings of the first main body 7 and the second main body 20. The 7 and the second main body 20 are fixed to the intermediate plate 45, respectively.

  The rear shaft end 4a of the first rotary shaft 4 and the front shaft end 17a of the third rotary shaft 17 are inserted into through holes 46 formed in the intermediate plate 45, respectively. Is inserted into the sleeve 30 in the through hole 46. Similarly, the rear shaft end 6a of the second rotation shaft 6 and the front shaft end 19a of the fourth rotation shaft 19 are respectively inserted into through holes 49 formed in the intermediate plate 45, Further, it is inserted into the sleeve 33 in the through hole 49.

  The outer peripheral surfaces of the shaft end 4 a of the first rotation shaft 4, the shaft end 6 a of the second rotation shaft 6, the shaft end 17 a of the third rotation shaft 17, and the shaft end 19 a of the fourth rotation shaft 19, Splines are formed in the respective axial directions, while splines are also formed in the inner peripheral surfaces of the sleeves 30 and 33 in the axial direction. The shaft end 4a of the first rotating shaft 4 and the shaft end 17a of the third rotating shaft 17 are inserted into the sleeve 30, respectively, and the splines mesh with each other, whereby the first rotating shaft 4 and the third rotating shaft 17 are engaged. Are connected so as to integrally rotate in the rotation direction. Similarly, the shaft end 6a of the second rotating shaft 6 and the shaft end 19a of the fourth rotating shaft 19 are inserted into the sleeve 33 and the splines mesh with each other, so that the second rotating shaft 6 and the fourth rotating shaft 19 are engaged. Are connected so as to integrally rotate in the rotation direction.

  Further, the shaft end 4a of the first rotating shaft 4 and the shaft end 17a of the third rotating shaft 17 are inserted through the drain holes 47 and 48 formed in the intermediate plate 45 in a state inserted into the sleeve 30, respectively. Tapered pins 31 and 32 are driven in, and first rotary shaft 4 and third rotary shaft 17 are interconnected by the action of taper pins 31 and 32 and sleeve 30 such that movement in the axial direction is integrated. Have been. Similarly, the shaft end 6a of the second rotation shaft 6 and the shaft end 19a of the fourth rotation shaft 19 are inserted through the drain holes 50 and 51 formed in the intermediate plate 45 while being inserted into the sleeve 33, respectively. The tapered pins 34 and 35 are driven into the second rotating shaft 6 and the fourth rotating shaft 19 by the action of the tapered pins 34 and 35 and the sleeve 33 so that the movements in the axial direction are integrated with each other. Are linked.

  A rear plate 55 is fixed to the rear end surface of the second main body 20, and the rear opening of the second main body 20 is sealed by the rear plate 55. The rear plate 55 has a stepped first cylinder hole having a large-diameter cylinder chamber 57 on the front side and a small-diameter cylinder chamber 58 on the rear side at a portion facing the rear end face of the third rotary shaft 17. A stepped first piston 59 having a large diameter on the front side and a small diameter on the rear side is inserted into the first cylinder hole 56, and the front end face of the first piston 59 is the third rotary shaft 17. Abut on the rear end face. Further, the working liquid leaked from the large-diameter cylinder chamber 57 and the small-diameter cylinder chamber 58 is appropriately discharged through a drain hole 68 formed in the rear plate 55.

  Similarly, a stepped second cylinder having a large-diameter cylinder chamber 63 on the front side and a small-diameter cylinder chamber 64 on the rear side is provided at a portion of the rear plate 55 facing the rear end surface of the fourth rotary shaft 19. A hole 62 is formed, and a stepped second piston 65 having a large diameter on the front side and a small diameter on the rear side is fitted into the second cylinder hole 62, and the front end surface thereof is connected to the fourth rotary shaft. 19 can be brought into contact with the rear end face. Further, the working liquid leaked from the large-diameter cylinder chamber 63 and the small-diameter cylinder chamber 64 is appropriately discharged through a drain hole 69 formed in the rear plate 55.

  Further, a first flow path 60 communicating with the high pressure side of the first hydraulic pressure chamber 8 and the large diameter cylinder chamber 57 of the first cylinder hole 56 is formed, and the high pressure side of the second hydraulic pressure chamber 21 and the first A second flow path 61 communicating with the small-diameter cylinder chamber 58 of the cylinder hole 56 is formed. Further, a third flow path 66 communicating with the high-pressure side of the first hydraulic chamber 8 and the large-diameter cylinder chamber 63 of the second cylinder hole 62 is formed, and the high-pressure side of the second hydraulic chamber 21 and the second A fourth flow path 67 communicating with the small-diameter cylinder chamber 64 of the cylinder hole 62 is formed.

  According to the hydraulic device 1 of the present example having the above-described configuration, when an electric motor is connected to the front end 4b of the first rotating shaft 4 and driven, the first gear 3 meshes with the first gear 3 thereby. The second gear 5 rotates, and the rotational power is transmitted to the third rotating shaft 17 connected thereto via the first rotating shaft 4, whereby the third gear 16 and the fourth gear meshing therewith are transmitted. The gear 18 rotates.

  When working fluid is supplied from the intake hole (not shown) to the low-pressure side of the first fluid pressure chamber 8 in order to use the first fluid pressure mechanism 2, the working fluid is supplied to the first gear 3. The pressure is increased to a high pressure by the action of the second gear 5 and discharged to the outside from a high pressure side through a discharge hole (not shown).

At this time, in the first hydraulic mechanism 2, the first gear 3 and the second gear 5 receive a thrust force by meshing with each other due to the meshing thereof, and the thrust force is received by the tooth surface receiving the pressure of the working liquid. Receive. Among these thrust forces, the pressure receiving thrust force acts on the tooth surfaces of the first gear 3 and the second gear 5 in the same manner, and therefore acts on the first gear 3 and the second gear 5 in the same direction. On the other hand, since the meshing thrust force is generated by the meshing of the teeth and acts as a mutual reaction force, it acts on the first gear 3 and the second gear 5 in opposite directions. In this example, the resultant force [F _pa1 + F _ma1 ] of the pressure receiving thrust force [F _pa1 ] and the meshing thrust force [F _ma1 ] both acts on the first gear 3 while the second gear 5 has: It is _assumed that the resultant force [F _pa1 −F _ma1 ] of the pressure receiving thrust force [F _pa1 ] directed backward and the meshing thrust force [−F _ma1 ] directed forward acts on the rear direction.

  In the hydraulic device 1 according to the present embodiment, the high pressure of the first hydraulic chamber 8 is supplied to the large-diameter cylinder chamber 57 of the first cylinder hole 56 formed in the rear plate 55 through the first flow path 60. The working liquid is supplied, whereby the first piston 59 is urged forward, and the third piston 17 is pressed forward by the first piston 59.

As described above, the first rotation shaft 4 and the third rotation shaft 17 rotate integrally in the rotation direction by the action of the taper pins 31 and 32 and the sleeve 30, and also integrally in the axial direction. Interconnected to move. Therefore, the pressing force of the first piston 59 is transmitted to the first rotating shaft 4 via the third rotating shaft 17, and the pressure receiving thrust force [F _pa1 ] acting on the first rotating shaft 4 and the meshing thrust The resultant force [F _pa1 + F _ma1 ] of the force [F _ma1 ] is reduced by the pressing force (drag force) of the first piston 59.

Incidentally, the drag given to the first and third rotating shafts 4 and 17 by the first piston 59 is determined by the pressure receiving thrust force [F _pa1 ] and the meshing thrust force [F _ma1 ] acting on the first rotating shaft 4. It is preferable that the large-diameter cylinder chamber 57 be balanced with the resultant force [F _pa1 + F _ma1 ] in accordance with the pressure of the working fluid on the high pressure side of the first hydraulic chamber 8 so as to _obtain such a drag. Is set as appropriate.

  On the other hand, the high-pressure working liquid in the first hydraulic chamber 8 is supplied to the large-diameter cylinder chamber 63 of the second cylinder hole 62 also formed in the rear plate 55 through the third flow path 66, The second piston 65 is urged forward, and the second piston 65 presses the fourth rotating shaft 19 forward.

As described above, the second rotation shaft 6 and the fourth rotation shaft 19 rotate integrally in the rotation direction by the action of the taper pins 34 and 35 and the sleeve 33, and also integrally in the axial direction. Interconnected to move. Therefore, the pressing force of the second piston 65 is transmitted to the second rotating shaft 6 via the fourth rotating shaft 19, and the pressure receiving thrust force [F _pa1 ] acting on the second rotating shaft 6 and the meshing thrust force resultant force towards the rear of the _{[-F ma1] [F pa1 -F} ma1] is relieved by the pressing force of the second piston 65 (drag).

Incidentally, the drag given to the second and fourth rotating shafts 6 and 19 by the second piston 65 is a pressure-receiving thrust force [F _pa1 ] acting on the second rotating shaft 6 and a meshing thrust force [−F _ma1 ]. It is preferable to balance the resultant force [F _pa1 −F _ma1 ] of the large-diameter cylinder according to the pressure of the working liquid on the high-pressure side of the first hydraulic pressure chamber 8 so as to _obtain such a drag. The effective diameter of the chamber 63 is appropriately set.

  On the other hand, in a state where the first and second gears 3 and 5 and the third and fourth gears 16 and 18 are rotated, the second hydraulic chamber 21 is used to use the second hydraulic mechanism 15. When the working liquid is supplied to the low-pressure side from its intake hole (not shown), the supplied working liquid is pressurized to a high pressure by the action of the third gear 16 and the fourth gear 18 and discharged from the high-pressure side. It is discharged outside through a hole (not shown).

At this time, in the second hydraulic mechanism 15, similarly, the third gear 16 and the fourth gear 18 are mutually meshed by the meshing and receive the thrust force, and the tooth surface receives the pressure of the working liquid. As a result, a thrust force is received. In this example, the resultant force [F _pa2 + F _ma2 ] of the pressure receiving thrust force [F _pa2 ] and the meshing thrust force [F _ma2 ] both acts on the third gear 16 while the fourth gear 18 has: _Assume that the resultant force [F _pa2 −F _ma2 ] of the pressure receiving thrust force [F _pa2 ] directed rearward and the meshing thrust force [−F _ma2 ] directed forward acts rearward.

In the hydraulic device 1 according to the present embodiment, the high-pressure operation of the second hydraulic chamber 21 through the second flow path 61 into the small-diameter cylinder chamber 58 of the first cylinder hole 56 formed in the rear plate 55. The liquid is supplied, whereby the first piston 59 is urged toward the front side, and the third piston 17 is pressed forward by the first piston 59. Thus, the resultant force [F _pa2 + F _ma2 ] of the pressure receiving thrust force [F _pa2 ] and the meshing thrust force [F _ma2 ] acting on the third rotating shaft 17 is reduced by the pressing force (drag force) of the first piston 59. .

The _reaction force applied to the third rotating shaft 17 by the first piston 59 is the resultant force [F _pa2 + F _ma2 ] of the pressure receiving thrust force [F _pa2 ] acting on the third rotating shaft 17 and the meshing thrust force [F _ma2 ]. The effective diameter of the small-diameter cylinder chamber 58 is appropriately set according to the pressure of the working fluid on the high-pressure side of the second hydraulic chamber 21 so as to obtain such a drag. .

On the other hand, the high-pressure working liquid of the second hydraulic chamber 21 is supplied to the small-diameter cylinder chamber 64 of the second cylinder hole 62 also formed in the rear plate 55 through the fourth flow passage 67, whereby The second piston 65 is biased toward the front side, and the fourth piston 19 is pressed forward by the second piston 65. Thus, the resultant force [F _pa1 −F _ma1 ] of the pressure receiving thrust force [F _pa2 ] and the meshing thrust force [−F _ma2 ] acting on the fourth rotating shaft 19 is applied to the pressing force of the second piston 65 ( (Drag).

Note that the drag given to the fourth rotating shaft 19 by the second piston 65 is the resultant force [F _pa1 -F] of the pressure receiving thrust force [F _pa2 ] acting on the fourth rotating shaft 19 and the meshing thrust force [F _ma2 ]. _ma1 ], and the effective diameter of the small-diameter cylinder chamber 64 is appropriately set according to the pressure of the working liquid on the high-pressure side of the second hydraulic chamber 21 so as to _obtain such a drag. I do.

  As described above, according to this hydraulic device 1, when each of the first hydraulic mechanism 2 and the second hydraulic mechanism 15 is used, the first rotary shaft 4 and the third rotary shaft 17 On the other hand, the first piston 59 acts on the thrust force acting on each of them to reduce the thrust force, and the thrust force acting on the second rotating shaft 6 and the fourth rotating shaft 19 respectively. Since the second piston 65 acts on the force against the force to reduce the thrust force, it is possible to suppress the above-described problem of vibration and leakage.

  A mechanism for imparting a drag to the first and third rotating shafts 4 and 17 is provided by a stepped first cylinder hole 56 formed in the rear plate 55, and a first piston inserted into the first cylinder hole 56. 59, a first flow passage 60 communicating between the high pressure side of the first hydraulic chamber 8 and the large diameter cylinder chamber 57 of the first cylinder hole 56, and the high pressure side of the second hydraulic chamber 21 and the first cylinder Since it is composed of the second flow path 61 communicating with the small-diameter cylinder chamber 58 of the hole 56, the structure is simpler and the number of parts is smaller than that of the above-described mechanism using the conventional compensation ring, and therefore the processing is Manufacturing costs including costs and assembly costs can be reduced.

  Further, in the hydraulic device 1, when performing maintenance such as replacement of parts of the mechanism for applying the above-described drag, only the rear plate 55 may be disassembled and reassembled. , Maintenance can be easily performed. Also, unlike the related art, since a sealing material or the like is not used to form the hydraulic chamber, the hydraulic device can be used at high speed.

  In the first embodiment, the first flow path 60 is formed so as to communicate with the large-diameter cylinder chamber 57 of the first cylinder hole 56 and the high-pressure side of the second hydraulic chamber 21. The passage 61 is formed so as to communicate with the small-diameter cylinder chamber 58 of the first cylinder hole 56 and the high-pressure side of the first hydraulic pressure chamber 8, and the third flow path 66 communicates with the large-diameter cylinder chamber 63 of the second cylinder hole 62. The fourth passage 67 is formed so as to communicate with the high-pressure side of the second hydraulic chamber 21, and the fourth flow path 67 is formed so as to communicate with the small-diameter cylinder chamber 64 of the second cylinder hole 62 and the high-pressure side of the first hydraulic chamber 8. It may be. According to such an embodiment, the same operation and effect as those of the hydraulic device of the first embodiment can be obtained.

[Second embodiment]
Next, a hydraulic device according to a second embodiment of the present invention will be described with reference to FIG. The hydraulic device 70 is a modification of the hydraulic device 1 according to the first embodiment described above. Therefore, in FIG. 2, the same components as those of the hydraulic device 1 according to the first embodiment are denoted by the same reference numerals, and detailed description thereof will be omitted below.

  As shown in FIG. 2, the hydraulic device 70 of the present example includes a second hydraulic shaft 15 ′ of a second gear 5 ′ provided in the first hydraulic mechanism 2 ′ and a second hydraulic mechanism 15 ′. This is a mode in which the fourth rotating shaft 19 'of the provided fourth gear 18' is not connected.

  In the hydraulic device 70, a third cylinder hole 71 serving as a cylinder chamber 72 is formed in a portion of the intermediate plate 45 'facing the rear end surface of the second rotating shaft 6'. A third piston 73 is fitted into the hole 71 so as to be able to contact the rear end face of the second rotating shaft 6 ′, and a fifth piston communicating with the cylinder chamber 72 and the high pressure side of the first hydraulic chamber 8. A channel 74 is formed.

  In the rear plate 55 ', a fourth cylinder hole 75 serving as a cylinder chamber 76 is formed at a portion facing the rear end surface of the fourth rotation shaft 19'. A fourth piston 77 is fitted into the rear end surface of the fourth rotating shaft 19 'so as to be able to abut, and further, a sixth flow path 78 communicating with the cylinder chamber 76 and the high pressure side of the second hydraulic chamber 21 is formed. Have been.

Thus, according to the hydraulic device 70, when the first hydraulic mechanism 2 ′ is used, the high-pressure working liquid in the first hydraulic chamber 8 is supplied through the fifth flow path 74. The fluid is supplied to the cylinder chamber 72 of the third cylinder hole 71, and the third piston 73 is urged forward by the working liquid, and the second piston 6 ′ is pressed forward by the third piston 73. By the pressing force of the third piston 3, the resultant force [F _pa1 ] of the thrust force (the received thrust force [F _pa1 ] and the thrust force [-F _ma1 ]) that acts rearward on the second rotating shaft 6 ′. −F _ma1 ]) is alleviated, thereby suppressing the problem of vibration and the problem of leakage due to the thrust force. Note that in this case, the third by the piston 73 and the second rotation axis 6 'drag applied to the said second axis of rotation 6' intended to balance the thrust force acting on the [F _{pa1 -F ma1]} Preferably, the effective diameter of the cylinder chamber 72 of the third cylinder hole 71 is appropriately set according to the pressure of the working liquid on the high pressure side of the first hydraulic chamber 8 so as to obtain such a drag. .

On the other hand, when using the second hydraulic mechanism 15 ′, the high-pressure working liquid in the second hydraulic chamber 21 is supplied to the cylinder chamber 76 of the fourth cylinder hole 75 through the sixth flow passage 78. Then, the fourth piston 77 is urged forward by the working liquid, and the fourth rotating shaft 19 ′ is pressed forward by the fourth piston 77. By the pressing force of the fourth piston 77, the resultant force [F _pa2 −F _ma2 ] of the thrust force acting on the fourth rotating shaft 19 ′ (the thrust force [−F _ma2 ] meshing with the pressure receiving thrust force [F _pa2 ]). ) Is reduced, thereby suppressing the problem of vibration and the problem of leakage caused by the thrust force. In this case, also in this case, the drag applied to the fourth rotating shaft 19 'by the fourth piston 77 balances the thrust force [F _pa1 -F _ma1 ] acting on the fourth rotating shaft 19'. Preferably, the effective diameter of the cylinder chamber 76 of the fourth cylinder hole 75 is appropriately set in accordance with the pressure of the working liquid on the high pressure side of the second hydraulic chamber 21 so as to obtain such a drag. .

[Third Embodiment]
Next, a hydraulic device according to a third embodiment of the present invention will be described with reference to FIG. The hydraulic device 80 is a further modification of the hydraulic device 70 according to the above-described second embodiment. Therefore, in FIG. 3, the same components as those of the hydraulic device 1 according to the first embodiment and the hydraulic device 70 according to the second embodiment are denoted by the same reference numerals, and the detailed description thereof will be described below. Omitted.

The thrust force acting on the second gear 5 ′ and the fourth gear 18 ′ may act forward or backward depending on the magnitude of the pressure receiving thrust and the engagement thrust. For example, when F _pa1 > F _ma1, a rearward thrust force [F _pa1 −F _ma1 ] acts on the second gear 5 ′, and when F _pa1 <F _ma1 , the second gear 5 ′. ′ Is _subjected to a forward thrust force [F _pa1 −F _ma1 ]. Similarly, when F _pa2 > F _ma2 , a thrust force [F _pa2 −F _ma2 ] toward the rear acts on the fourth gear 18 ′, and when F _pa2 <F _ma2 , the fourth gear 18 ′ A forward thrust force [F _pa2 −F _ma2 ] acts on 18 ′.

  In the hydraulic device 1 according to the first embodiment and the hydraulic device 70 according to the second embodiment described above, the thrust force toward the rear is applied to the second gears 5, 5 'and the fourth gears 18, 18'. In this case, the hydraulic device 80 according to the present embodiment corresponds to the case where a forward thrust force acts on the second gear 5 ′ and the fourth gear 18 ′.

  As shown in FIG. 3, in the hydraulic device 80, a fifth cylinder hole 81 serving as a cylinder chamber 82 is formed in a portion of the front plate 40 ′ facing the front end surface of the second rotating shaft 6 ′. At the same time, a fifth piston 83 is fitted into the fifth cylinder hole 81 so as to be able to come into contact with the front end face of the second rotary shaft 6 ′. Further, the cylinder chamber 82 of the fifth cylinder hole 81 and the first A seventh flow path 84 communicating with the high pressure side of the hydraulic chamber 8 is formed.

  In the intermediate plate 45 ″, a sixth cylinder hole 85 serving as a cylinder chamber 86 is formed at a portion facing the front end surface of the fourth rotation shaft 19 ′. A sixth piston 87 is fitted into the front end surface of the rotating shaft 19 ′ so as to be able to contact the same, and an eighth flow passage 88 communicating with a cylinder chamber 86 of the sixth cylinder hole 85 and a high pressure side of the second hydraulic chamber 21. Is formed.

According to the hydraulic device 80, when using the first hydraulic mechanism 2 ′, the high-pressure working liquid in the first hydraulic chamber 8 is supplied to the fifth cylinder hole 81 through the seventh passage 84. Is supplied to the cylinder chamber 82, and the fifth piston 83 is urged rearward by the working liquid, and the second rotating shaft 6 ′ is pressed rearward by the fifth piston 83. Then, the thrust force [F _pa1 −F _ma1 ] acting on the second rotating shaft 6 ′ is reduced by the pressing force of the fifth piston 83, whereby the problem of vibration caused by the thrust force and the leakage The problem is suppressed. In this case, also in this case, the drag given to the second rotating shaft 6 'by the fifth piston 83 is balanced with the thrust force [F _pa1 -F _ma1 ] acting on the second rotating shaft 6'. Preferably, the effective diameter of the cylinder chamber 82 of the fifth cylinder hole 81 is appropriately set according to the pressure of the working liquid on the high pressure side of the first hydraulic chamber 8 so as to obtain such a drag.

On the other hand, when using the second hydraulic mechanism 15 ′, the high-pressure working liquid in the second hydraulic chamber 21 is supplied to the cylinder chamber 86 of the sixth cylinder hole 85 through the eighth flow passage 88, The sixth piston 87 is urged rearward by the working liquid, and the sixth piston 87 presses the fourth rotation shaft 19 ′ rearward. The thrust force [F _pa2 −F _ma2 ] acting on the fourth rotation shaft 19 ′ is reduced by the pressing force of the sixth piston 87, whereby the problem of vibration due to the thrust force and the leakage The problem is suppressed. In this case, also in this case, the drag given to the fourth rotating shaft 19 'by the sixth piston 87 is balanced with the thrust force [F _pa2 -F _ma2 ] acting on the fourth rotating shaft 19'. Preferably, the effective diameter of the cylinder chamber 86 of the sixth cylinder hole 85 is appropriately set according to the pressure of the working liquid on the high pressure side of the second hydraulic chamber 21 so as to obtain such a drag.

In this hydraulic device 80, when a rearward thrust force [F _pa1 -F _ma1 ] acts on the second gear 5 ′, the fifth cylinder hole 81 provided in the front plate 40 ′ and the fifth piston The third cylinder hole 71, the third piston 73, and the fifth channel 74 may be provided in the intermediate plate 45 ', as in the above-described hydraulic device 70, instead of the 83 and the seventh channel 84.

When a rearward thrust force [F _pa1 -F _ma1 ] acts on the fourth gear 18 ′, the sixth cylinder hole 85, the sixth piston 87, and the eighth flow path provided in the intermediate plate 45 ″ are provided. Instead of 88, a configuration in which the fourth cylinder hole 75, the fourth piston 77, and the sixth flow path 78 are provided in the rear plate 55 "as in the hydraulic device 70 described above may be used.

[Fourth embodiment]
Next, a hydraulic device according to a fourth embodiment of the present invention will be described with reference to FIG. The hydraulic device 90 is a further modification of the hydraulic device 70 according to the second embodiment described above. Therefore, in FIG. 4, the same components as those of the hydraulic device 1 according to the first embodiment and the hydraulic device 70 according to the second embodiment are denoted by the same reference numerals, and the detailed description thereof will be described below. Omitted.

  As shown in FIG. 4, the hydraulic device 90 of the present example is different from the hydraulic device 70 of the second embodiment in that the first rotary shaft 4 ′ of the first gear 3 ′ and the third The structure is different in that the rotary shaft 17 is directly connected.

  That is, as shown in FIG. 4, in the hydraulic device 90 of the present example, a spline hole is formed in the rear end of the first rotary shaft 4 ′ on the rear side, and the rear end in which the spline hole is formed is It is configured to be inserted into a through hole 92 formed in the intermediate plate 91, and the front end 17a of the third rotating shaft 17 is inserted into the spline hole from the opposite side. Further, the rear end of the first rotary shaft 4 'and the front end 17a of the third rotary shaft 17 are connected by a tapered pin 32' which is driven through a drain hole 93, whereby the first rotary shaft 4 ' The third rotary shaft 17 is connected to each other so as to rotate integrally in the rotational direction and move integrally in the axial direction.

  The hydraulic device 90 configured as described above has the same operation and effect as the hydraulic device 70 described above.

In this hydraulic device 90, when a forward thrust force [F _pa1 −F _ma1 ] acts on the second gear 5 ′, the third cylinder hole 71 provided in the intermediate plate 90 and the third piston Instead of the 73 and the fifth flow path 74, a configuration in which the fifth cylinder hole 81, the fifth piston 83, and the seventh flow path 84 are provided in the front plate 40 as in the above-described hydraulic device 80 is preferable.

When a forward thrust force [F _pa1 -F _ma1 ] acts on the fourth gear 18 ′, the fourth cylinder hole 75, the fourth piston 77, and the sixth passage provided in the rear plate 55 ′ are provided. Instead of 78, a configuration in which the sixth cylinder hole 85, the sixth piston 87, and the eighth flow path 88 are provided in the intermediate plate 90 as in the above-described hydraulic device 80 may be used.

[Fifth Embodiment]
Next, a hydraulic device according to a fifth embodiment of the present invention will be described with reference to FIG. The hydraulic device 100 is a further modification of the hydraulic device 70 according to the above-described second embodiment. Therefore, in FIG. 5, the same components as those of the hydraulic device 70 according to the second embodiment are denoted by the same reference numerals, and a detailed description thereof will be omitted below.

  As shown in FIG. 5, in this hydraulic device 100, the rotation shaft of the first gear 3 ″ and the rotation shaft of the third gear 16 ′ are formed from a single shaft body to form the same rotation shaft 4 ″. In this respect, the configuration is largely different from the hydraulic device 70. Other configurations are dimensionally different, but there is no major difference in the basic configuration.

  In the figure, reference numeral 101 denotes an intermediate plate, and an intermediate portion of the rotary shaft 4 "is inserted into a through hole 102 formed in the intermediate plate 101. Reference numeral 18" denotes a fourth gear, and reference numeral 19 denotes a fourth gear. "Is a fourth rotating shaft, 20 'is a second main body, 21' is a second hydraulic chamber, 22 'is a third bearing member, 24' is a fourth bearing member, 23 '. Is a third side plate, reference numeral 25 'is a fourth side plate, and reference numeral 55' '' is a rear plate.

  The hydraulic device 100 configured as described above has the same operation and effect as the hydraulic device 70 described above.

In the hydraulic device 100, when a forward thrust force [F _pa1 −F _ma1 ] acts on the second gear 5 ′, the third cylinder hole 71 provided in the intermediate plate 101, the third piston Instead of the 73 and the fifth flow path 74, a configuration in which the fifth cylinder hole 81, the fifth piston 83, and the seventh flow path 84 are provided in the front plate 40 as in the above-described hydraulic device 80 is preferable.

When a forward thrust force [F _pa1 −F _ma1 ] acts on the fourth gear 18 ″, the fourth cylinder hole 75, the fourth piston 77 and the sixth piston 77 provided in the rear plate 55 ′ ″ are provided. Instead of the flow path 78, a configuration in which the sixth cylinder hole 85, the sixth piston 87, and the eighth flow path 88 are provided in the intermediate plate 101 as in the above-described hydraulic device 80 may be used.

  As described above, the specific embodiments of the present invention have been described, but the embodiments that the present invention can adopt are not limited to these embodiments.

  As an example, the hydraulic devices 1, 70, 80, 90, and 100 of the above-described embodiments are respectively hydraulic pumps, but the hydraulic device according to the present invention is not limited to this. And a mode as a hydraulic motor.

DESCRIPTION OF SYMBOLS 1 Hydraulic device 2 1st hydraulic mechanism part 3 1st helical gear (1st gear)
4 First rotating shaft 5 Second helical gear (second gear)
6 Second rotating shaft 7 First main body 8 First hydraulic chamber 9 First bearing member 11 Second bearing member 15 Second hydraulic mechanism 16 Third helical gear (third gear)
17 Third rotating shaft 18 Fourth helical gear (fourth gear)
19 fourth rotating shaft 20 second main body 21 second hydraulic chamber 22 third bearing member 24 fourth bearing member 40 front plate 45 intermediate plate 55 rear plate 56 first cylinder hole 57 large-diameter cylinder chamber 58 small-diameter cylinder chamber 59 1st piston 60 1st flow path 61 2nd flow path 62 2nd cylinder hole 63 large diameter cylinder chamber 64 small diameter cylinder chamber 65 2nd piston 66 3rd flow path 67 4th flow path

Claims (3)

A hydraulic device configured by juxtaposing a first hydraulic mechanism and a second hydraulic mechanism,
A first helical gear having a first rotating shaft; a second helical gear having a second rotating shaft, meshing with the first helical gear; A first main body having a first hydraulic chamber in which a portion is opened and in which the first and second helical gears are housed in an engaged state; and wherein the first and second helical gears in the first hydraulic chamber are provided. First and second bearing members rotatably supporting a rotating shaft, one of the first hydraulic chambers being a low pressure side and the other being a meshing portion of the first and second helical gears. Is set to the high pressure side,
A second helical gear having a third rotating shaft; a fourth helical gear having a fourth rotating shaft meshing with the third helical gear; A second main body having a second hydraulic chamber in which a portion is opened and in which the third and fourth helical gears are housed in a meshing state; Third and fourth bearing members rotatably supporting a rotating shaft, one of the second hydraulic chambers being on the low pressure side and the other being on the boundary of the meshing portion of the third and fourth helical gears. Is set to the high pressure side,
Further, the first and second hydraulic mechanisms are arranged side by side so that at least the first rotation axis and the third rotation axis are located coaxially, and between the first main body and the second main body. Is provided with an intermediate plate, the first and second main bodies are fixed to the intermediate plate, and the other opening of the first main body, which is the front opening, is sealed by the front plate, The rear opening, which is the other opening of the second body, is sealed by a rear plate,
A front shaft portion of the first rotation shaft extends through the front plate and extends to the outside, and a rear shaft end of the first rotation shaft and a front shaft end of the third rotation shaft. The parts are respectively inserted into through holes formed in the intermediate plate, and connected so as to rotate integrally,
In the first hydraulic mechanism, a combined force of a thrust force caused by the engagement of the first and second helical gears and a thrust force caused by the high-pressure side working liquid acts rearward on the first rotating shaft. At the same time, in the second hydraulic mechanism, the combined force of the thrust force due to the meshing of the third and fourth helical gears and the thrust force due to the working fluid on the high pressure side is directed backward with respect to the third rotating shaft. In a hydraulic device configured to operate,
The rear shaft end of the first rotation shaft and the front shaft end of the third rotation shaft are connected to each other such that movement in the axial direction is also integrated,
In the rear plate, a stepped first cylinder hole having a large-diameter cylinder chamber on the front side and a small-diameter cylinder chamber on the rear side is formed in a portion facing the rear end surface of the third rotating shaft. In addition, a stepped first piston having a large diameter on the front side and a small diameter on the rear side is fitted into the first cylinder hole so that the front end surface thereof can abut on the rear end surface of the third rotary shaft. ,
Further, a first flow path communicating with the high-pressure side of the first hydraulic chamber and one of the large-diameter cylinder chamber and the small-diameter cylinder chamber of the first cylinder hole is formed, and the high-pressure side of the second hydraulic chamber is formed. And a second flow passage communicating with the other of the large-diameter cylinder chamber and the small-diameter cylinder chamber of the first cylinder hole. The hydraulic device according to claim 1, wherein the first rotation shaft and the third rotation shaft are configured by one shaft instead of being integrally connected . The first and second hydraulic mechanisms are arranged side by side such that the second rotation axis and the fourth rotation axis are coaxially located,
A rear shaft end of the second rotation shaft and a front shaft end of the fourth rotation shaft are respectively inserted into through holes formed in the intermediate plate, and rotate integrally with each other. It is interconnected so that movement in the axial direction is also integrated,
In the first hydraulic mechanism, a combined force of a thrust force caused by the engagement of the first and second helical gears and a thrust force caused by the high-pressure side working liquid acts rearward on the second rotating shaft. At the same time, in the second hydraulic mechanism, the combined force of the thrust force due to the meshing of the third and fourth helical gears and the thrust force due to the working liquid on the high pressure side is directed rearward with respect to the fourth rotating shaft. Configured to work,
A stepped second cylinder hole having a large-diameter cylinder chamber on the front side and a small-diameter cylinder chamber on the rear side is formed in the rear plate at a portion facing the rear end face of the fourth rotary shaft. A stepped second piston having a large diameter on the front side and a small diameter on the rear side is fitted into the second cylinder hole so that the front end surface thereof can abut on the rear end surface of the fourth rotary shaft. ,
A third flow path communicating with the high-pressure side of the first hydraulic chamber and one of the large-diameter cylinder chamber and the small-diameter cylinder chamber of the second cylinder hole is formed, and the high-pressure side of the second hydraulic chamber is connected to the third hydraulic passage. large-diameter cylinder chamber and the hydraulic system according to claim 1 Symbol mounting, characterized in that the fourth channel leading to the other of the small-diameter cylinder chamber is formed in the second cylinder bore.

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