KR20010104927A - Hydraulic pump having valve - Google Patents

Abstract

The present invention relates to an integrated valve hydraulic pump, comprising an oil inflow passage through which hydraulic oil flows, a first and a second oil discharge passage through which oil is discharged, and an oil flow passage communicating with the first and second oil discharge passages. A main block having a flow path switching means; A first driving gear, a first driven gear, and a first block installed on one side of the main block; A first motor for rotating the first drive and the first driven gear; A second driving gear, a second driven gear, and a second block provided on the other side of the main block; And a second motor for rotating the second driving gear and the second driven gear, and oil flow port ports are formed at left and right sides of the engagement portion of the first driving gear and the first driving gear, respectively. It is characterized in that the oil flow port port is formed in each of the upper and lower teeth of the driven gear.

The hydraulic pump of the present invention made as described above has a structure in which two pairs of gears provided in one block assembly allow hydraulic oil to flow, thereby reducing the size and weight of the device and reducing power loss.

Description

Valve integrated hydraulic pump {Hydraulic pump having valve}

The present invention relates to a hydraulic pump with a built-in gear, and more particularly to a valve-integrated hydraulic pump that is provided with one inlet and two outlets to control and operate two actuators at the same time.

A belt transmission device, which is one of power transmission means for transmitting power generated from a power source, is provided with a belt that connects and winds the drive pulley and the driven pulley and the drive pulley and the driven pulley.

In addition to the basic function of transmitting power, the belt transmission device includes a device having a continuously variable function capable of controlling the rotational speed between the drive shaft and the driven shaft by adjusting the interval of the pulley.

As means for adjusting the spacing of the pulleys, a hydraulic pump and an actuator driven by the hydraulic pump are used. In the related art, the hydraulic pump is directly connected to the engine shaft, so that a sufficient amount of flow rate can be supplied even when the engine rotation is slow. Since the pump capacity must be used, there is a limit that the flow rate loss of the hydraulic oil is large when the engine rotation is fast. In addition, since the hydraulic oil pumped at the maximum pressure is supplied to each actuator using a pressure reducing valve, there is a problem that a pressure loss is caused.

SUMMARY OF THE INVENTION The present invention has been made to solve the above problems, and includes two pairs of gears in one block assembly and configured to allow each of the gears to flow hydraulic oil, so that the size and weight of the device is small and the power loss is small. The purpose is to provide a pump.

1 is a view showing a belt transmission device to explain an application example of a valve-integrated hydraulic pump according to an embodiment of the present invention.

Figure 2 is an exploded perspective view showing the configuration of the valve-integrated hydraulic pump according to an embodiment of the present invention.

Figure 3 is a perspective view schematically showing a main block constituting a valve-integrated hydraulic pump according to an embodiment of the present invention.

Figure 4 is a view showing for explaining the internal configuration of the valve-integrated hydraulic pump according to an embodiment of the present invention.

Figure 5 is a cross-sectional view showing a flow path switching means inside the valve-integrated hydraulic pump according to an embodiment of the present invention.

6 is a cross-sectional view taken along the line VI-VI of FIG. 5.

7 is a view for explaining the operation of the flow path switching means of the valve-integrated hydraulic pump according to an embodiment of the present invention.

8 is a view showing another example of the valve-integrated hydraulic pump according to an embodiment of the present invention.

<Explanation of symbols for the main parts of the drawings>

10: oil tank 12: hydraulic pump

14: 2nd motor 16: 1st motor

17: drive shaft 18: pump block

20: actuator 22: belt

24: moving pulley flight 26, 69: first block

28: oil seal 29: oil seal mounting groove

30: Through hole 32: First drive gear

34: 1st driven gear 36: Gear shaft

38, 71: Main block 40: first oil discharge passage

41: 2nd oil discharge path 42, 57: gear mounting cavity

44, 45: Oil flow zone 48, 49: Gear shaft support groove

50: 2nd Drive Gear 52: 2nd Drive Gear

53: Gear Shaft Support Groove 54: Through Hole

56, 70: 2nd block 58, 59: gear shaft support groove

62,63: Oil groove 64: Oil inflow passage

65: oil flow path 66: spool

67: annular projection 68: oil passage

74: driven pulley 76: driven pulley

79: locking jaw 80, 82: gear mounting cavity

88: connecting passage

The present invention has been made in order to achieve the above object, the oil inflow passage in which the hydraulic oil flows, and the oil supplied to the external actuator is discharged and in communication with each other and the first oil discharge passage provided with a flow path switching means in the communication unit And a second oil discharge passage communicating with the first and second oil discharge passages through the flow path switching means and connected to an oil inflow passage so that oil introduced from the outside passes through the flow path switching means. A main block having an oil flow passage for flowing into an oil discharge passage, and an oil flow opening communicating with the first and second oil discharge passages, respectively; A first block coupled to one side of the main block and having a through hole formed therein; A first driving gear and a first driven gear installed between the first block and the main block and rotatably engaged with each other; A first motor coupled to the first driving gear through the through hole of the first block to rotate the first driving gear and the first driven gear; A second block coupled to the other side of the main block and having a through hole formed therein; A second driving gear and a second driven gear which are rotatably engaged with each other between the second block and the main block; And a second motor coupled to the second driving gear through the through hole of the second block to rotate the second driving gear and the second driven gear, and the ports of the oil flow opening are the first driving gear and the first driven drive. Located on both sides of the geared portion of the gear, oil flows into and out of the oil flow opening by rotation of the first driving gear and the first driven gear, and the ports of the oil flow passage and the ports of the oil inflow passage are respectively the second driving gear. Located on both sides of the engagement portion of the second driven gear is characterized in that the oil flows into the oil flow path and the oil inflow passage by the rotation of the second drive gear and the second driven gear.

In addition, the first oil discharge passage and the second oil discharge passage are formed in a straight line in the main block, and the communication portion is a cylindrical projection formed on the inner circumferential surface of the first and second oil discharge passage, and the first oil discharge passage and A second oil discharge passage is partitioned and a plurality of oil passages communicating with the oil flow passage are formed on the inner circumferential surface thereof in a longitudinal direction, and the flow path switching means is fitted to allow the reciprocating motion to the inner region of the cylindrical protrusion, The loop-shaped annular protrusion is integrally formed, and includes a spool blocking the oil passage by the annular protrusion according to the reciprocating motion.

In addition, a gear mounting cavity for inserting the first driving gear and the first driven gear is formed on one side of the main block in contact with the first block, the inside of the gear mounting cavity of the first driving gear and the first driven gear A gear shaft supporting groove into which a gear shaft is inserted and a port of the oil flow opening are positioned, and a gear shaft supporting groove and a through hole supporting the gear shaft of the first driven gear and the gear shaft of the first driving gear are located in the first block. Is formed,

Gear mounting cavity for inserting the second drive gear and the second driven gear is formed on the other side of the main block in contact with the second block, the gear shaft of the second drive gear and the second driven gear inside the gear mounting cavity The insertion shaft support groove is formed, and the port of the oil flow path and the port of the oil inflow passage are located, and the second block supports the gear shaft of the second driven gear and the gear shaft of the second driving gear in the second block. Characterized in that the gear shaft support groove and the through-hole is formed.

In addition, a gear mounting cavity in which the first driving gear and the first driven gear are engaged with each other is formed on an opposing surface of the first block in contact with the main block, and a gear shaft supporting groove is formed inside the gear mounting cavity. And a through hole, a gear shaft supporting groove for supporting the gear shaft of the first driving gear and the first driven gear and a port of both oil flow ports are formed on the opposite surface of the main block in contact with the first block.

On the opposing surface of the second block in contact with the main block, a gear mounting cavity is formed in which the second driving gear and the second driven gear are engaged with each other, and a gear shaft supporting groove and the gear mounting cavity are formed inside the gear mounting cavity. A through hole is provided, and a gear shaft supporting groove for supporting a gear shaft of the second driving gear and the second driven gear is formed on an opposite surface of the main block in contact with the second block, and an oil flow passage port and an oil inflow passage port. Characterized in that formed.

Hereinafter, the present invention will be described in more detail with reference to the accompanying drawings.

1 is a view showing a state in which the valve integral hydraulic pump according to an embodiment of the present invention is applied to a conventional belt transmission apparatus capable of continuously variable speed.

Referring to the drawings, the driving pulley 74 and the driven pulley 76 are connected by the belt 22, the actuator 20 is connected to each pulley (74, 76) to drive the hydraulic pump 12 Speed ratio control is achieved. The drive pulley 74 and the driven pulley 76 are variable pulleys each composed of two pulley sheaves. The two pulley pieces are composed of a fixed pulley piece 23 and a moving pulley piece 24, the fixed pulley piece 23 is fixed to the drive shaft or driven shaft to rotate only, the moving pulley piece 24 drive shaft Or it is installed to be axially slidable to the driven shaft to adjust the rotation radius of the belt wound by moving forward and backward relative to each fixed pulley piece (23).

An actuator 20 is provided in each of the moving pulley pieces 24. The actuator 20 receives the hydraulic pressure from the valve-integrated hydraulic pump 12 of the present invention to move the moving pulley piece 24.

The hydraulic pump 12 has a first drive and a first driven gear (32, 34 in Fig. 2) and a second drive and a second driven gear (50, 52 in Fig. 2) is built and the hydraulic flow path is formed A pump block 18, a first motor 16 for rotating the first driving gear 32, and a second motor 14 for rotating the second driving gear 50 are included.

As will be described later, the second motor 14 is a motor that provides a low pressure among the two actuators 20, and the first motor 16 is a motor that provides a high pressure. In addition, when the hydraulic oil is supplied to one actuator, the hydraulic oil is drawn out from the other actuator.

The hydraulic pump 12 is connected to the oil tank 10 in which hydraulic oil is stored.

2 is an exploded perspective view illustrating the configuration of a valve integrated hydraulic pump according to an exemplary embodiment of the present invention.

Referring to the drawings, the hydraulic pump according to the present embodiment is coupled to the main block 38 and the first block 26 coupled to one side of the main block 38 and the other side of the main block 38. A second block 56 is included. In addition, between the first block 26 and the main block 38, the first drive gear 32 and the first driven gear 34 are rotatably coupled to each other, and the main block 38 and the first block 38 are rotatable. Between the two blocks 56, the second driving gear 50 and the second driven gear 52 are rotatably installed in an engaged state.

The gear shaft 36 provided in the first drive gear 32 is shaft-coupled with the drive shaft 17 of the first motor 16. Accordingly, when the first motor 16 is driven, the first driving gear 32 and the first driven gear 34 rotate to perform a function of a gear pump as described below. Similarly, when the second drive gear 50 is coupled to the drive shaft 17 of the second motor 14 and the second motor 14 is driven, the second drive gear 50 and the second driven gear 52 rotate. To flow the hydraulic oil.

The first driving gear 32 and the first driven gear 34 are positioned up and down with respect to each other. That is, the first driven gear 34 is engaged with and positioned at the upper portion of the first driving gear 32 connected to the drive shaft 17. In contrast, the second driving gear 50 and the second driven gear 52 are located to the left and right with respect to each other. That is, the second driven gear 52 is engaged with the second driving gear 50.

On the other hand, the main block 38 is formed with a plurality of flow paths in which hydraulic oil flows and communicates with each other, the bottom of the port of the oil inflow passage (64 in Fig. 4), both sides of the first oil discharge passage 40 A port and a port of the second oil discharge passage (41 in FIG. 3) are formed. The oil inflow passage 64 is connected to an external oil tank (10 of FIG. 1).

The first oil discharge passage 40 and the second oil discharge passage 41 are connected to each actuator 20. Therefore, when the oil is supplied to the corresponding actuator through the discharge passage on one side, the oil that has been supplied to the other actuator in the meantime exits by the volume corresponding to the retraction amount of the moving pulley piece and flows into the discharge passage on the other side.

As described above, the first block 26 is coupled to the main block 38 with the first driving gear 32 and the first driven gear 34 interposed therebetween. At this time, a sealing member may be installed so that oil does not leak between the close contact surfaces between the main block 38 and the first block 26.

The first block 26 is formed with a through hole 30 through which the gear shaft 36 of the first drive gear 32 penetrates, and an oil groove 62 is provided on the inner circumferential surface of the through hole 30. . The oil groove 62 is a passage provided to return the leaking hydraulic oil to the oil inflow passage (64 in FIG. 4).

In addition, an oil chamber mounting groove 29 is formed on an outer surface of the through hole 30. The oil chamber 28 is inserted into the oil chamber mounting groove 29. The oil chamber 28 prevents hydraulic oil flowing in the blocks 26 and 38 from being leaked to the outside through a gap between the gear shaft 36 and the through hole 30 of the first driving gear 32. The sealing member to flow to the oil inflow passage 64 through the oil groove (62).

In addition, the shaft coupling method of the gear shaft 36 and the first motor 16 of the first driving gear 32 penetrating the through hole 30 and the oil chamber 28 may be implemented in various ways known in the art. Can be.

On the inner side of the first block 26 facing the main block 38, a gear shaft support groove (48 in FIG. 4) is formed so that the gear shaft 36 of the first driven gear 34 is inserted and supported. .

Meanwhile, a gear mounting cavity 42 is formed on one side of the main block 38 in contact with the first block 26. The gear mounting cavity 42 is a groove formed in one side of the main block 38, and the first driving gear 32 and the first driven gear 34 are accommodated in a state where they are engaged to rotate. to be.

In the gear mounting cavity 42, the gear shaft supporting grooves 48 and 49 and the ports of the oil flow ports 44 and 45 are formed. The upper gear shaft support groove 48 of the gear shaft support grooves 48 and 49 is a groove supporting the gear shaft 36 of the first driven gear 34. The lower gear shaft support groove 49 is a groove supporting the gear shaft 36 of the first drive gear 32.

Ports of the oil flow openings 44 and 45 are formed at both sides of the central portion of the gear mounting cavity 42. The oil flow openings 44 and 45 extend into the main block 38 so that the oil flow opening 44 on one side communicates with the second oil discharge passage 41 (see FIG. 5), and the other oil flow openings 45 1 communicates with the oil discharge passage 40.

Therefore, when the first driving gear 32 and the first driven gear 34 are installed in the gear mounting cavity 42 and the main block 38 and the first block 26 are combined, the gear mounting cavity 42 is It is sealed and serves as a chamber. Since the gear mounting cavity 42 is in communication with the oil flow openings 44 and 45 and the first drive gear 32 is connected to the first motor 16, one gear pump is formed. At this time, depending on the rotation direction of the drive shaft 17 of the first motor 16, the oil may enter the oil flow port 44 and go out to 45, or may enter the oil flow port 45 and exit to 44.

Meanwhile, as shown in the drawing, a port of the first oil discharge passage 40 is formed on the side of the main block 38, and a second oil discharge passage is formed on the side opposite to the first oil discharge passage 40. The port of 41) of 3 is formed. As will be described later, the first oil discharge passage 40 and the second oil discharge passage 41 form a straight line in the interior of the main block 38 to communicate with each other, but the spool (66) of FIG. ) Is installed. The spool 66 determines the flow rate and direction of oil flowing into the first oil discharge passage 40 and the second oil discharge port 41.

The second block 56 is formed with a gear shaft supporting groove 53 for supporting the gear shaft 36 of the second driven gear 52. In addition, a through hole 54 is formed next to the gear shaft support groove 53. The through hole 54 is a hole through which the gear shaft 36 of the second driving gear 50 penetrates, and an oil chamber 28 is provided on an outer surface thereof. The oil chamber 28 functions like the oil chamber provided in the first block 26.

In addition, the oil groove 63 is formed on the inner circumferential surface of the through hole 54. The oil groove 63 also has the same function as the oil groove 62 formed in the first block 26 and is connected to the oil inflow passage 64. The gear shaft 36 of the second drive gear 50 is shaft-connected with the drive shaft 17 of the second motor 14 through the through hole 54 and the oil chamber 28 of FIG.

3 is a view illustrating a gear mounting cavity formed in a main block to install the second driving gear and the second driven gear.

As shown, a gear mounting cavity 57 is formed on the other side of the main block 38, which is a space accommodated in a state where the second driving gear 50 and the second driven gear 52 are engaged with each other. Gear shaft support grooves 58 and 59 are formed in the gear mounting cavity 57 at right and left sides. The gear shaft supporting grooves 58 and 59 are grooves for supporting the gear shaft 36 of the second driving gear 50 and the second driven gear 52. The gear shaft supporting grooves 58 on the left side of the drawing The gear shaft of the second drive gear 50 is inserted, and the other gear shaft supporting groove 59 is a groove into which the gear shaft of the second driven gear 52 is inserted.

A port of the oil flow passage 65 and a port of the oil inflow passage 64 are formed at the center upper and lower portions of the gear mounting cavity 57.

Therefore, when the second driving gear 50 and the second driven gear 52 are installed in the gear mounting cavity 57 and the main block 38 and the second block 56 are combined, the gears 50 and 52 are installed. ) And a gear pump having an oil flow passage 65 and an oil inflow passage 64. At this time, if the second drive gear 50 rotates in the direction of arrow a in FIG. 2, the flow of hydraulic oil in the gear mounting cavity 57 flows out of the port of the oil inflow passage 64 to the port of the oil flow passage 65. Will enter.

Ports of the second oil discharge passage 41 are formed on the side of the main block 38.

Figure 4 is a view showing for explaining the internal configuration of the valve-integrated hydraulic pump according to an embodiment of the present invention.

The same reference numerals as the above reference numerals denote the same members having the same function.

Referring to the drawings, it can be seen that the first drive gear 32 is in shaft engagement with the drive shaft 17 of the first motor 16 in a state of meshing with the first driven gear 34. In addition, the lower portion of the first driving gear 32 is formed so that the oil groove 62 is inclined. The oil groove 62 is provided in the first block 26 and the main block 38, respectively, and is formed to communicate with each other when the first block 26 and the main block 38 are combined.

The second drive gear 50 is also connected to the drive shaft 17 of the second motor 14. It can be seen that the oil inflow passage 64 is formed at the lower side of the second driving gear 50 and the second driven gear (52 in FIG. 2) and the oil flow passage 65 is formed at the upper side thereof. In addition, the second groove 56 is provided with an oil groove 63.

As a result, the oil flow openings 44 and 45, the oil flow passage 65, the oil inflow passage 64, the first oil discharge passage (40 in FIG. 2) and the second oil discharge passage ( 41 in FIG. 3 is formed to communicate with each other.

The oil inflow passage 64 is a passage for receiving oil from the outside into the main block 38 and is connected to the inside of the gear mounting cavity 57. In addition, the oil flow path 65 is a passage through which the oil flowing out by being pressurized while passing through the gear mounting cavity 57 flows.

Therefore, when the second drive gear 50 rotates in the arrow a direction of FIG. 2, the oil flows in the oil flow path 65 in the arrow b direction. When the second motor 14 is rotated in reverse, the flow direction of oil is reversed.

Also in the first driving gear 32 and the first driven gear 34, the flow of oil through the oil flow openings 44 and 45 is directed according to the rotation direction of the first driving gear 32. When the first drive gear 32 is rotated in the direction of arrow c of FIG. 2, the oil filled in the gear mounting cavity 42 flows in the direction of arrow d of FIG. 2 and flows into the oil flow port 45. Likewise, it is supplied to an actuator (not shown) connected to the outside through the first oil discharge passage 40 of FIG. 5. When the rotation direction of the first drive gear 32 is rotated in reverse, the oil flows to the other actuator via the oil flow opening 44 via the second oil discharge passage 41.

On the other hand, the hydraulic oil flowing along the direction of the arrow b flows only to the first oil discharge passage 40 or only to the second oil discharge passage 41 according to the operation of the spool 66, or the first oil discharge passage ( 40) and the second oil discharge passage (41).

That is, in the state in which the spool (66 in FIG. 5) is located in the center as described below with reference to FIG. 5, the hydraulic oil flows evenly distributed between the first oil discharge passage 40 and the second oil discharge passage 41. . In addition, when the spool 66 moves toward the first oil discharge passage 40 or moves to the second oil discharge passage 41, the flow of oil changes.

FIG. 5 shows the oil flow passage 65 in the main block 38, the first and second oil discharge passages 40 and 41, the oil flow openings 44 and 45 and the spool 66 at the same time. to be.

Oil is always filled in the oil flow passage 65, the first oil discharge passage 40, the second oil discharge passage 41, and the oil flow openings 44 and 45. In this state, when the second motor 14 or the first motor 16 is driven, the movement of oil is started to cause the actuator to move the moving pulley piece.

The oil flow passage 65 is connected to the first oil discharge passage 40 and the second oil discharge passage 41 through an oil passage 68 provided on the inner circumferential surface of the locking jaw 79. Therefore, the hydraulic oil may flow in the first oil discharge passage 40 or the second oil discharge passage 41 according to the movement of the spool 66 along the arrow e direction.

In addition, the oil passages 68 are communicated with each other by the connection passage (88). The connection passage 88 is a flow passage of hydraulic oil for communicating each oil passage 68.

The locking jaw 79 is a cylindrical protrusion formed integrally with the inner circumferential surface of the central portion of the first oil discharge passage 40 and the second oil discharge passage 41, and the upper portion thereof is bored by the oil flow passage 65. A cylindrical spool 66 is installed in the inner region of the locking jaw 79. In addition, the oil passage 68 in the longitudinal direction is formed on the inner circumferential surface of the locking jaw 79. Therefore, when the spool 66 is inserted into the locking jaw 79, the oil may flow through the oil passage 68.

The spool 66 may be linearly moved in the direction of the arrow e in the locking jaw 79. Moreover, the annular projection part 67 is integrally formed in the outer peripheral surface of the both ends of the spool 66, respectively. The annular protrusion 67 is a circular protrusion having a larger diameter than the central portion of the spool 66, and is in close contact with the locking jaw 79 to serve as a cover for blocking the oil passage 68.

The separation distance between the annular projections 67 on both sides is longer than the length of the locking step 79. Therefore, the annular projection 67 is selectively in contact with the engaging jaw (79) at the same time. That is, when the spool 66 moves to the right side in the drawing, the annular projection on the left side comes into contact with the engaging jaw 79, and vice versa.

Accordingly, the oil flowing downward through the oil flow passage 65 in the state where the spool 66 is located at the center portion passes through the oil passage 68 and passes through the first oil discharge passage 40 and the second oil discharge passage 41. And the same force on the actuator.

6 is a cross-sectional view taken along the line VI-VI of FIG. 5.

Referring to the drawings, the locking jaw 79 is integrally formed on the inner circumferential surfaces of the first and second oil discharge passages 40 and 41, and a cylindrical spool 66 is formed in the inner region of the locking jaw 79. You can see that it is installed. In addition, four oil passages 68 are provided on the inner circumferential surface of the locking jaw 79. Although four oil passages 68 are formed in the figure, the size and number of the oil passages 68 may of course vary depending on embodiments. However, the oil passage 68 must be in communication with the oil flow passage (65).

In addition, the radius of the oil passage 68 from the central axis of the spool 66 is r1, the radius of the annular projection 67 of the spool 66 is r2, the first and second oil discharge passage (40, 41) When the radius is r3, it can be seen that r2 is larger than r1 and smaller than r3. This allows the annular projection 67 to reciprocate without contacting the inner circumferential surfaces of the first and second oil discharge passages 40 and 41, and also allow the annular projection 67 to block the oil passage 68 through linear movement. It means that there is.

7 is a view showing for explaining the internal operation of the valve-integrated hydraulic pump according to an embodiment of the present invention.

When the first oil discharge passage 40 in the figure is connected to the drive side actuator 20 and the second oil discharge passage 41 is connected to the driven actuator, FIG. 7 provides hydraulic power to the drive side actuator. If it is.

First, as shown in FIG. 5, when the first driving gear (32 in FIG. 2) is rotated in the direction of arrow c in the state where oil is filled in each flow port, the oil is arrowed in FIG. 2 inside the gear mounting cavity 42. It flows in the d direction and exits the oil flow port 45, part of which flows in the direction of arrow d in FIG. 7 and part of which flows through the oil passage 68 along the direction of arrow g, moving the spool in the direction of arrow f and It flows to the flow port 44. This flow continues until the oil passage 68 is blocked.

In addition, the oil flows in or out through the oil flow path 65 at the same time as the flow of the oil as described above.

When the oil passage 68 is completely blocked, the oil flowing through the oil flow passage 65 moves to the drive side actuator through the first oil discharge passage 40 to push the actuator to the moving pulley. That is, the oil supplied through the oil flow path (65) flows through the oil passage (68) to one oil flow opening (44), and passes through the first drive gear (32) and the first driven gear (34). The oil flow port 45 exits in the direction of the arrow d and moves to the actuator.

At the same time, the rod of the driven actuator should be retracted. This means that the hydraulic oil in the driven actuator passes through the second oil discharge passage 41 and passes through the first and driven gears 32 and 34 through the oil flow opening 44. It is possible because it exits. At this time, since the amount of movement of the driven side and the drive side actuator is different, the oil is replenished through the oil flow path 65 when the amount of movement on the drive side is large, and when the amount of movement on the driven side is large, the oil flows out through the oil flow path 65. I'm going.

On the other hand, when the pressures of the two actuators are different, the hydraulic pressure flows back into the gap between the gears 32 and 34 and the cavity, so that the pressure difference becomes small. Therefore, since the magnitude of the pressure difference is determined according to the force and the speed of driving the gears 32 and 34, the first motor can control the magnitude of the pressure difference by controlling the current or the voltage using a DC motor. The same applies to the case of the second motor and the gear mounting cavity 57.

In order to move both moving pulley pieces 24 in opposite directions as the driving conditions change, the rotation direction of the first motor 16 is changed. When the rotational direction of the first motor 16 is changed, the rotational direction of the first driving gear 32 and the first driven gear 34 is changed, and the spool 66 is moved to the left in the drawing so that the locking jaw 79 The oil passage 68 is blocked, and the flow of oil is directed on the same principle as above to determine the desired position of the actuator.

8 is a view showing another example of a hydraulic pump according to an embodiment of the present invention.

The same reference numerals as the above reference numerals refer to the same members having the same function, and thus description thereof will be omitted.

Referring to the drawings, it can be seen that the first driving gear 32 and the first driven gear 34 are provided on the side of the first block 69. That is, the gear mounting cavity 80 for installing the first driving gear 32 and the second driving gear 34 is formed on the opposing surface of the first block 69 instead of the main block 71. . On the mating surface of the main block 71 with the first block 69, oil flow holes 44 and 45 communicating with the gear shaft support grooves 48 and 49 and the gear mounting cavity 80 are formed.

In addition, a gear mounting cavity 82 for installing the second driving gear 50 and the second driven gear 52 is provided in the second block 70. In addition, a port and oil of the oil inflow passage 64 connected to the inner surface of the gear shaft support grooves 58 and 59 and the gear mounting cavity 82 are coupled to the second block 70 of the main block 71. The flow path 65 is formed.

As mentioned above, although this invention was demonstrated in detail through the specific Example, this invention is not limited to the said Example, A various deformation | transformation is possible for a person with ordinary knowledge within the scope of the technical idea of this invention.

The hydraulic pump of the present invention made as described above has a structure in which two pairs of gears provided in one block assembly allow hydraulic oil to flow, so that the size and weight of the device can be controlled with small power. .

Claims (4)

The oil inflow passage 64 into which the hydraulic oil flows and the oil supplied to the external actuator are discharged and communicate with each other, and the communication portion has a first oil discharge passage 40 and a second oil discharge passage provided with a flow path switching means. 41) and the first and second oil discharge passage (40, 41) and the oil inflow passage (64) through the flow path switching means and the oil introduced from the outside through the flow path switching means first And oil flow passages 65 for flowing into the second oil discharge passages 40 and 41, and oil flow holes 44 and 45 communicating with the first and second oil discharge passages 40 and 41, respectively. Main blocks 38 and 71; First blocks 26 and 69 coupled to one side of the main blocks 38 and 71 and having through holes 30 formed therein; A first driving gear 32 and a first driven gear 34 interposed between the first blocks 26 and 69 and the main blocks 38 and 71 and rotatably interlocked with each other; A first motor is coupled to the first drive gear 32 through the through holes 30 of the first blocks 26 and 69 to rotate the first drive gear 32 and the first driven gear 34. 16); Second blocks 56 and 70 coupled to the other sides of the main blocks 38 and 71 and having through holes 54 formed therein; A second driving gear (50) and a second driven gear (52) which are rotatably engaged with each other between the second blocks (56, 70) and the main blocks (38, 71); A second motor which is shaft-connected with the second driving gear 50 through the through holes 54 of the second blocks 56 and 70 to rotate the second driving gear 50 and the second driven gear 52; 14) Ports of the oil flow openings 44 and 45 are located at both sides of the engagement portion of the first driving gear 32 and the first driven gear 34 so that the first driving gear 32 and the first driven gear 34 The oil flows into and out of the oil flow openings 44 and 45 by rotation, and the ports of the oil flow passage 65 and the ports of the oil inflow passage 64 are respectively the second driving gear 50 and the second driven gear ( 52 are located on both sides of the engagement portion of the second drive gear 50 and the second driven gear 52 by the rotation of the oil flow path 65 and the oil inlet passage 64 is characterized in that the oil flows in and out Valve-integrated hydraulic pump. The method of claim 1, The first oil discharge passage 40 and the second oil discharge passage 41 are formed in a straight line in the main blocks 38 and 71, and the communication portion has the first and second oil discharge passages 40 and 41. As a cylindrical protrusion formed on the inner circumferential surface of the first oil discharge passage 40 and the second oil discharge passage 41, the inner circumferential surface has a plurality of oil passages 68 communicating with the oil flow passage 65 in length It is formed in the direction, the flow path switching means is fitted in the inner region of the cylindrical projection so as to reciprocate movement, the annular projection portion 67 of the loop type is formed integrally on both outer peripheral surfaces of the annular projection portion 67 in accordance with the reciprocating motion Valve integral hydraulic pump, characterized in that it comprises a spool blocking the oil passage (68). The method of claim 2, A gear mounting cavity 42 for inserting the first driving gear 32 and the first driven gear 34 is formed on one side of the main block 38 in contact with the first block 26, and the gear mounting cavity Gear shaft support grooves 48 and 49 into which the first drive gear 32 and the gear shaft 36 of the first driven gear 34 are inserted are supported inside the 42 and the oil flow holes 44 and 45. Is located in the first block 26, the gear shaft support groove 48 for supporting the gear shaft 36 of the first driven gear 34 and the gear shaft 36 of the first drive gear 32. ) And through holes 30 are formed, A gear mounting cavity 57 for inserting the second driving gear 50 and the second driven gear 52 is formed on the other side of the main block 38 in contact with the second block 56, and the gear mounting cavity Inside the 57, gear shaft support grooves 58 and 59 are formed, in which the second drive gear 50 and the second drive gear 52 of the gear shaft 36 are inserted and supported, and the oil flow path 65 ) And a port of the oil inflow passage 64, the second block 56, the gear shaft 36 of the second driven gear 52 and the gear shaft 36 of the second drive gear 50 The valve integral hydraulic pump, characterized in that the gear shaft support groove 53 and the through hole 54 for supporting). The method of claim 2, On the opposite surface of the first block 69 in contact with the main block 71, a gear mounting cavity 80 is formed in which the first driving gear 32 and the first driven gear 34 are engaged with each other. A gear shaft support groove 48 and a through hole 30 are provided in the gear mounting cavity 80, and the first drive is provided on an opposite surface of the main block 71 in contact with the first block 69. The gear shaft supporting grooves 48 and 49 supporting the gear shaft 36 of the gear 32 and the first driven gear 34 and the ports of both oil flow ports 44 and 45 are formed. On the opposite surface of the second block 70 in contact with the main block 71, a gear mounting cavity 82 is formed in which the second driving gear 50 and the second driven gear 52 are engaged with each other. In the gear mounting cavity 82, gear shaft supporting grooves 58 and 59 and the through hole 54 are provided, and on the opposite surface of the main block 71 in contact with the second block 70, Gear shaft support grooves 58 and 59 for supporting the gear shaft 36 of the second drive gear 50 and the second driven gear 52 are formed, and the oil flow path 65 port and the oil inflow passage ( 64) Valve integrated hydraulic pump, characterized in that the port is formed.