阅读说明：本技术 液压泵 (Hydraulic pump ) 是由 赤见俊也 于 2019-04-29 设计创作，主要内容包括：本发明提供一种液压泵,其能够减小驱动源的起动转矩。液压泵(10)包括：缸体(30),其具有多个缸孔(32),且被配置为能够旋转；活塞(38),其移动自如地保持在各缸孔(32)内；斜板(40),其根据偏转角的大小来控制活塞(38)的移动量；第1推压部件(50),其用于朝向斜板(40)的偏转角变小的方向推压斜板(40)；以及第2推压部件(60),其用于在从外部供给来的压力的作用下朝向斜板(40)的偏转角变大的方向推压斜板(40)。(The present invention provides a kind of hydraulic pump, can reduce the starting torque of driving source.Hydraulic pump (10) includes: cylinder body (30), with multiple cylinder holes (32), and is configured to rotate；Piston (38) is movably maintained in each cylinder holes (32)；Inclined plate (40), the amount of movement of piston (38) is controlled according to the size of deflection angle；1st push part (50), the direction for being used to become smaller towards the deflection angle of inclined plate (40) push inclined plate (40)；And the 2nd push part (60), it is used to push inclined plate (40) towards the direction that the deflection angle of inclined plate (40) becomes larger under the action of being externally supplied the pressure come.)

1. a kind of hydraulic pump, wherein

The hydraulic pump includes:

Cylinder body with multiple cylinder holes, and is configured to rotate；

Piston is movably maintained in each cylinder holes；

Inclined plate controls the amount of movement of the piston according to the size of deflection angle；

1st push part, the direction for being used to become smaller towards the deflection angle of the inclined plate push the inclined plate；And

2nd push part is used to become larger under the action of being externally supplied the pressure come towards the deflection angle of the inclined plate Direction pushes the inclined plate.

2. hydraulic pump according to claim 1, wherein

The pushing that there is 2nd push part direction for becoming larger towards the deflection angle of the inclined plate to push the inclined plate Bar,

The pressure acts on the end face of the side opposite with the inclined plate of the push strut.

3. hydraulic pump according to claim 1 or 2, wherein

The pressure is pressure corresponding with inverted flux control pressure.

4. hydraulic pump according to claim 1 or 2, wherein

The pressure is pressure corresponding with load-transducing flow control pressure.

5. hydraulic pump according to claim 1 or 2, wherein

The pressure is pressure corresponding with positive flow control pressure.

6. hydraulic pump according to claim 1 or 2, wherein

The pressure is pressure corresponding with locking rod pressure.

7. hydraulic pump according to claim 1 or 2, wherein

The pressure be by electric signal using electromagnetic proportional valve be converted into it is hydraulic obtained from pressure.

Technical field

The present invention relates to a kind of hydraulic pumps for construction vehicle etc..

Background technique

In the extensive field such as construction vehicle, hydraulic pump has been used.As an example, hydraulic pump includes rotary shaft；Cylinder Body is formed with multiple cylinder holes extended along rotary axis direction；Piston is movably maintained in each cylinder holes；Inclined plate, It is used to make each piston move in each cylinder holes when cylinder body rotates；And mechanism, for changing inclined plate relative to cylinder body The inclination angle (deflection angle) of rotary shaft.Rotary shaft links with the engine as driving source.In particular, above-mentioned hydraulic pump is also made For the use of capacity-variable type hydraulic pump.Such capacity-variable type hydraulic pump is disclosed in Japanese JP2002-138948A An example.

The hydraulic pump exports the driving force generated based on oil from the discharge of cylinder holes.More specifically, using from starting The power of machine rotates rotary shaft, so that the cylinder body in conjunction with rotary shaft be made to rotate, and makes piston reciprocating by the rotation of cylinder body Movement.According to the reciprocating action of the piston, oil and other cylinder holes sucking oil are sprayed from a part of cylinder holes, thus hydraulic pump obtains To realize.At this point, inclined plate is deflected in such a way that its deflection angle becomes larger by push part such as the springs being located in pump case, root is utilized The push part such as the control piston acted according to the pressure of input deflect in such a way that its deflection angle becomes smaller.It is inclined with inclined plate Corner becomes larger, and oil becomes larger from the discharging jet amount of hydraulic pump.

Disclosed in the Japanese JP2002-138948A in the case where previous hydraulic pump, in engine start, not to Control piston input pressure, therefore the deflection angle of inclined plate is maximum.That is, torque required for driving hydraulic pump is maximum.In the feelings Under condition, in order to start engine and start the driving of hydraulic pump, biggish driving force is needed.In particular, oily at low ambient temperatures Viscosity can become larger, therefore start engine required for driving torque become very large.Therefore, low temperature ring is in hydraulic pump In the case where the use of border, it is sometimes desirable to be increased the processing such as size of battery, starter motor for starting engine etc..

Summary of the invention

The present invention allows for such aspect and is made into, and its purpose is to provide one kind can reduce rising for driving source The hydraulic pump of dynamic torque.

Hydraulic pump of the invention includes:

Cylinder body with multiple cylinder holes, and is configured to rotate；

Piston is movably maintained in each cylinder holes；

Inclined plate controls the amount of movement of the piston according to the size of deflection angle；

1st push part, the direction for being used to become smaller towards the deflection angle of the inclined plate push the inclined plate；And

2nd push part is used to become under the action of being externally supplied the pressure come towards the deflection angle of the inclined plate Big direction pushes the inclined plate.

In hydraulic pump of the invention, it is also possible to

There is 2nd push part direction for becoming larger towards the deflection angle of the inclined plate to push pushing away for the inclined plate Compression bar,

The pressure acts on the end face of the side opposite with the inclined plate of the push strut.

In hydraulic pump of the invention, it is also possible to

The pressure is pressure corresponding with inverted flux control pressure.

In hydraulic pump of the invention, it is also possible to

The pressure is pressure corresponding with load-transducing flow control pressure.

In hydraulic pump of the invention, it is also possible to

The pressure is pressure corresponding with positive flow control pressure.

In hydraulic pump of the invention, it is also possible to

The pressure is pressure corresponding with locking rod pressure.

In hydraulic pump of the invention, it is also possible to

The pressure be by electric signal using electromagnetic proportional valve be converted into it is hydraulic obtained from pressure.

The effect of invention

Using the present invention, it is possible to provide one kind can reduce the hydraulic pump of the starting torque of driving source.

Detailed description of the invention

Fig. 1 is the figure for illustrating one embodiment of the present invention.In particular, Fig. 1 is to indicate that the deflection angle of inclined plate is minimum When hydraulic pump section figure.

Fig. 2 is the figure for indicating the section of the hydraulic pump of Fig. 1 in the deflection angle maximum of inclined plate.

Fig. 3 A is the figure of the pressure of the 2nd push part for illustrating to be input to hydraulic pump.

Fig. 3 B is the figure of the pressure of the 2nd push part for illustrating to be input to hydraulic pump.

Fig. 4 A is the figure for indicating a variation of hydraulic pump, and is the 2nd push part for illustrating to be input to hydraulic pump Pressure figure.

Fig. 4 B is the figure for illustrating to be input to the pressure of the 2nd push part of hydraulic pump together with Fig. 4 A.

Fig. 5 A is the figure for indicating another variation of hydraulic pump, and is the 2nd pressing portion for illustrating to be input to hydraulic pump The figure of the pressure of part.

Fig. 5 B is the figure for illustrating to be input to the pressure of the 2nd push part of hydraulic pump together with Fig. 5 A.

Fig. 6 A is the figure for indicating another variation of hydraulic pump, and is the 2nd pressing portion for illustrating to be input to hydraulic pump The figure of the pressure of part.

Fig. 6 B is the figure for illustrating to be input to the pressure of the 2nd push part of hydraulic pump together with Fig. 6 A.

Fig. 6 C is the figure for illustrating to be input to the pressure of the 2nd push part of hydraulic pump together with Fig. 6 A and Fig. 6 B.

Fig. 7 A is the figure for indicating another variation of hydraulic pump, and is the 2nd pressing portion for illustrating to be input to hydraulic pump The figure of the pressure of part.

Fig. 7 B is the figure for illustrating to be input to the pressure of the 2nd push part of hydraulic pump together with Fig. 7 A.

Fig. 8 A is the figure for indicating another variation of hydraulic pump, and is the 2nd pressing portion for illustrating to be input to hydraulic pump The figure of the pressure of part.

Fig. 8 B is the figure for illustrating to be input to the pressure of the 2nd push part of hydraulic pump together with Fig. 8 A.

Specific embodiment

Hereinafter, being illustrated referring to attached drawing to one embodiment of the present invention.In addition, the attached drawing appended by this specification In, for the ease of illustration and understand, and carried out change relative to suitably comparative example ruler and asperratio etc. in kind, overstated .

In addition, for use in the present specification shape, geometric condition and determine they degree for example The terms such as " parallel ", " orthogonal ", " identical ", length, value of angle etc., are not limited to the stringent meaning, can be construed to include It can expect the range of the degree of same function.

FIG. 1 to FIG. 8 B is the figure for illustrating one embodiment of the present invention.Wherein, Fig. 1 and Fig. 2 is to indicate hydraulic pump 10 Section figure.In particular, Fig. 1 is the section for indicating the hydraulic pump 10 when the deflection angle (inclination angle) of aftermentioned inclined plate 40 is minimum Figure, the figure in the section of the hydraulic pump 10 when Fig. 2 is the deflection angle maximum for indicating inclined plate 40.

The hydraulic pump 10 of present embodiment is so-called ramp type capacity-variable type hydraulic pump.The output of hydraulic pump 10 is based on oil The driving force generated from the discharge (and the sucking of oil to cylinder holes 32) of aftermentioned cylinder holes 32.More specifically, using come spontaneous The power of the power sources such as motivation rotates rotary shaft 25, so that the cylinder body 30 combined by spline combination etc. with rotary shaft 25 be made to revolve Turn, and 38 reciprocating action of piston is made by the rotation of cylinder body 30.According to the reciprocating action of the piston 38, sprayed from a part of cylinder holes 32 It is fuel-displaced and suck oil to other cylinder holes 32, so that hydraulic pump is achieved.

Fig. 1 and hydraulic pump shown in Fig. 2 10 have shell 20, rotary shaft 25, cylinder body 30, inclined plate 40, the 1st push part 50 And the 2nd push part 60.

Shell 20 is had the 1st outer housing 21 and is combined using secure component (not shown) etc. with the 1st outer housing 21 The 2nd outer housing 22.Shell 20 is accommodated with the part of rotary shaft 25, cylinder body 30, inclined plate 40 and the 1st push part 50.In Fig. 1 and It in example shown in Fig. 2, is configured in the inside of the 1st outer housing 21: the one end of rotary shaft 25, via suction plate 35 and multiple cylinders The suction inlet and outlet (not shown) of the connection of hole 32, the 1st guide portion 23 for guiding aftermentioned push strut 61.Also, it inhales Entrance is arranged through 21 ground of the 1st outer housing, is connected to the hydraulic power source (tank) for the outside for being set to hydraulic pump 10.

The rotary shaft recess portion 24a being inserted into for rotary shaft 25 is formed in the 1st outer housing 21, rotary shaft 25 is used in rotary shaft It is supported in recess portion 24a using bearing 28a to be rotated freely around axis (rotation axis) Ax.Axis Ax along rotary shaft 25 length Direction extends.

It is formed in the 2nd outer housing 22 for the perforative rotary shaft hole 24b of rotary shaft 25, rotary shaft 25 is from one end direction The other end extends through cylinder body 30 and 40 ground of inclined plate.Rotary shaft 25 utilizes the axis for being configured at rotary shaft hole 24b in its other end 28b bearing is held to rotate freely around axis Ax.In the example of diagram, the other end spin shaft of rotary shaft 25 is outside with hole 24b Side is prominent, links by power sources such as the spline engaging portion 26b and engine for being formed in the other end.In addition, it is not limited to This, the other end shaft that do not spin for being also possible to rotary shaft 25 is protruded outward with hole 24b.That is, being also possible to rotary shaft 25 The other end be located at the inside of shell 20.For example, it can be the drive shaft that ultromotivity source extends is inserted into shell 20, should The other end of drive shaft and rotary shaft 25 links in shell 20.

In Fig. 1 and example shown in Fig. 2, rotary shaft 25 be set to through cylinder body 30 part spline engaging portion 26c with 30 spline of cylinder body combines.By in conjunction with the spline of the cylinder body 30, rotary shaft 25 can on the direction of axis Ax with cylinder body 30 It independently moves, but is integrally rotated together on the direction of rotation around axis Ax with cylinder body 30.In addition, rotary shaft 25 is the 1st It is supported to rotate freely using bearing 28a in outer housing 21, be limited using bearing 28b along axis in the 2nd outer housing 22 Moving and being supported to rotate freely for the direction of line Ax, does not contact with inclined plate 40.Thus, rotary shaft 25 is set as can It is not rotated together to around the direction of rotation of axis Ax with cylinder body 30 with interfering by the component in addition to cylinder body 30.

Cylinder body 30 is configured to rotate centered on axis Ax together with rotary shaft 25, and has and run through around axis Ax The multiple cylinder holes 32 being equipped with.In particular, each cylinder holes 32 is set as respectively along flat with axis Ax in Fig. 1 and example shown in Fig. 2 Capable direction extends.In addition, being not limited thereto, it is also possible to cylinder holes 32 and is provided along relative to the inclined side of axis Ax To extension.The quantity for being formed in multiple cylinder holes 32 of cylinder body 30 is not particularly limited, it is preferred that from the side along axis Ax To when being observed, these cylinder holes 32 are configured on the same circumference with (equiangularly spaced) at equal intervals.

It is formed with respectively and in multiple cylinder holes 32 in the end of the side opposite with the setting side of inclined plate 40 of cylinder body 30 Each cylinder holes 32 be connected to opening 32a.Also, the end with the side opposite with the setting side of inclined plate 40 of cylinder body 30 is practised physiognomy It is configured with suction plate 35 over the ground, which is formed with multiple through holes (not shown).Multiple cylinder holes 32 are via the opening 32a and through hole are connected to the suction inlet and outlet (not shown) being located in the 1st outer housing 21, via the suction inlet and row Outlet carries out the sucking and discharge of oil.In addition, in Fig. 1 and example shown in Fig. 2, rotary shaft 25 be located at cylinder body 30 with set It sets and is formed with around the end of the opposite side in side of inclined plate 40 for storing aftermentioned spring 44 and seat 45a, 45b Recess portion 30a.

Fig. 1 and suction plate 35 shown in Fig. 2 are fixed on the 1st outer housing 21, and even if cylinder body 30 with rotary shaft 25 together It is static also relative to shell 20 (the 1st outer housing 21) in the case where rotation.Therefore, the cylinder being respectively communicated with suction inlet and outlet Hole 32 switches according to the rotation status of cylinder body 30 by suction plate 35, is discharged from the state of suction inlet sucking oil with to outlet Switch repeatedly between the state of oil.

Piston 38 is configured as moving freely relative to respectively corresponding cylinder holes 32.In other words, piston 38 moves freely Ground is maintained in respective corresponding cylinder holes 32.In particular, each piston 38 be set as can relative to corresponding cylinder holes 32 along The direction parallel with axis Ax moves back and forth.The inside of piston 38 is cavity, is filled up by the oil in cylinder holes 32.Thus, piston 38 Reciprocating motion it is associated to the sucking of cylinder holes 32 and from the discharge of cylinder holes 32 with oil, it is oily when piston 38 is from the pull-out of cylinder holes 32 It is sucked from suction inlet into cylinder holes 32, when piston 38 enters in cylinder holes 32, oil is discharged from cylinder holes 32 to outlet.

In the present embodiment, in the end by 40 side of inclined plate of each piston 38 (from the end of the side outstanding of cylinder holes 32) Piston shoes 43 are installed.Also, spring 44, seat 45a, 45b, coupling member 46, pressing member 47 are equipped with around rotary shaft 25 And piston shoes holding member 48.Spring 44 and seat 45a, 45b are incorporated in recess portion 30a, and recess portion 30a is formed in rotary shaft 25 Be located at cylinder body 30 with around the end of the opposite side in the setting side of inclined plate 40.In Fig. 1 and example shown in Fig. 2 In, spring 44 is helical spring, is configured in recess portion 30a with compressing the state between present 45a and seat 45b.Thus, spring 44 Pushing force is generated using the direction that its elastic force is extended to the spring 44.The pushing force of spring 44 is via seat 45b and coupling member 46 transmit to pressing member 47.Piston shoes holding member 48 remains each piston shoes 43, pushing force of the pressing member 47 by spring 44, And each piston shoes 43 are pressed towards inclined plate 40 by piston shoes holding member 48.

In Fig. 1 and example shown in Fig. 2, inclined plate 40 can be with various angular deflections, but the work of the pushing force in spring 44 Under, each piston shoes 43 independently can suitably follow inclined plate 40 with the deflection angle of inclined plate 40 and be pressed against inclined plate 40.As a result, when When piston 38 rotates together with cylinder body 30, each piston shoes 43 are mobile in a manner of drawing circular orbit on inclined plate 40.In addition, illustrating Example in, the glomerate protrusion of end shape by 40 side of inclined plate of piston 38, piston 38 protrusion insertion is formed in piston shoes 43 Spherical recess portion, the recess portion of piston shoes 43 form spherical bearing construction by piston 38 and piston shoes 43 by caulked.Utilize the spherical bearing Construction, even if the deflection angle of inclined plate 40 changes, each piston shoes 43 can also follow the deflection of inclined plate 40 and fit on inclined plate 40 The mobile rotation in locality.

Inclined plate 40 controls the amount of movement of piston 38 according to the size of its deflection angle.Specifically, inclined plate 40 is with cylinder body 30 rotate around axis Ax and move each piston 38 in each cylinder holes 32.Inclined plate 40 has flat in the side faced with cylinder body 30 Interarea 41, be pressed against interarea 41 by the piston shoes 43 that the end of inclined plate 40 side links with piston 38.Also, inclined plate 40 is set For that can deflect, the stroke of the reciprocating motion of piston 38 changes according to the deflection angle of inclined plate 40 (interarea 41).That is, inclined plate 40 The deflection angle of (interarea 41) is bigger, then occur with the reciprocating motion of each piston 38 oil relative to cylinder holes 32 soakage and Discharge rate is bigger, and the deflection angle of inclined plate 40 (interarea 41) is smaller, then the oily phase occurred with the reciprocating motion of each piston 38 For cylinder holes 32 soakage and discharge rate with regard to smaller.Here, the deflection angle of inclined plate 40 (interarea 41) refers to the plate face of inclined plate 40 Angle formed by (interarea 41) imaginary plane orthogonal with axis Ax.In the case where deflection angle is 0 degree, even if cylinder body 30 is around axis Line Ax rotation, each piston 38 also do not move back and forth, oil from the discharge rate of each cylinder holes 32 be also zero.In addition, as shown in Figure 1, for Inclined plate 40 can abut if its deflection angle reduces with the stop part 27 for being set to the 2nd outer housing 22.Stop part 27 is configured to It is enough to retreat relative to inclined plate 40.The Minimum deviation angle of inclined plate 40 can be by making stop part 27 retreat relative to inclined plate 40 as a result, To suitably adjust.In addition, inclined plate 40 has acting surface 42, the acting surface 42 and aftermentioned push strut 61 in the outside of interarea 41 It abuts, and the pushing force of push strut 61 acts on the acting surface 42.In the example of diagram, acting surface 42 is set as flat with interarea 41 Row.

The direction that 1st push part 50 is used to become smaller towards the deflection angle of inclined plate 40 pushes inclined plate 40.In Fig. 1 and Fig. 2 institute In the example shown, the 1st push part 50 include configuration the 1st 51 of the side (1st outer housing 21 side) opposite with inclined plate 40, Configure at the 2nd 52 of 40 side of inclined plate (22 side of the 2nd outer housing) and configure spring 54 between the 1st 51 and the 2nd 52, 55.1st spring 54 is configured between the 1st 51 and the 2nd 52 with the state of compression.Thus, the 1st spring 54 utilizes its elastic force The direction extended towards the 1st spring 54 generates pushing force.2nd spring 55 is configured in the inside of the 1st spring 54.Therefore, the 2nd bullet The coil diameter of spring 55 is formed as smaller than the coil diameter of the 1st spring 54.

In Fig. 1 and example shown in Fig. 2, the 2nd spring 55 is fixed on the 2nd 52, in the lesser shape of the deflection angle of inclined plate 40 State leaves the 1st 51 under (referring to Fig.1).As a result, when the deflection angle of inclined plate 40 is smaller, the only pushing force effect of the 1st spring 54 In inclined plate 40.If the deflection angle of inclined plate 40 becomes larger, in a certain deflection angle, the 2nd spring 55 is contacted with the 1st 51.If tiltedly The deflection angle of plate 40 is further enlarged (referring to Fig. 2), then the 2nd spring 55 is also compressed between the 1st 51 and the 2nd 52, by This, the pushing force of 55 the two of the 1st spring 54 and the 2nd spring acts on inclined plate 40.Thus, utilize the 1st push part of diagram 50, the pushing force can be made periodically to change according to the deflection angle of inclined plate 40.In addition, the 2nd spring 55 is not limited to fix In the 2nd 52, it can also be fixed on the 1st 51, the 1st 51 and the 2nd any one of 52 can also be not secured to, and can It is moved between the 1st 51 and the 2nd 52.In the example of diagram, the 1st 51 relative to the 2nd 52 separated separation distance energy It is enough to be adjusted by making adjuster 57 retreat towards the 1st 51.Thereby, it is possible to suitably adjust the 1st push part 50 Initial pushing force, the especially initial pushing force based on the 1st spring 54 of the 1st push part 50.In addition, in present embodiment In, the 2nd spring 55 is arranged to assign additional pushing force to the 1st spring 54.Thus, according to the 1st pressing portion of expectation The pushing force characteristic that part 50 plays, can also omit the 2nd spring 55.

2nd push part 60 acts on the pushing force being oppositely directed to the 1st push part 50 to the pushing force of inclined plate 40 Inclined plate 40.In particular, the 2nd push part 60 resists the direction of the 1st push part 50 to become smaller towards the deflection angle of inclined plate 40 Pushing force, and the direction to become larger towards the deflection angle of inclined plate 40 pushes inclined plate 40.In Fig. 1 and example shown in Fig. 2, the 2nd is pushed Component 60 has push strut 61 and is formed in the pressure chamber 65 of the side opposite with inclined plate 40 of push strut 61.It is externally supplied and Pressure input (importing) pressure chamber 65.In addition, in the present specification, " outside " refers to the outside of hydraulic pump 10.Push strut 61 It is pushed using the pressure for being input to pressure chamber 65 towards inclined plate 40, and inclined plate 40 is made to become larger around its clinoid with deflection angle Mode deflects.That is, the 2nd push part 60 is controlled using the pressure for being input to the 2nd push part 60 (pressure chamber 65).

In Fig. 1 and example shown in Fig. 2, push strut 61 is whole to have generally cylindrical shape, with its axis and axis Ax parallel mode and the acting surface 42 of inclined plate 40 configure face to face.In addition, push strut 61 be not limited to its axis with Axis Ax parallel mode configures, can also by its axis relative to axis Ax it is inclined in a manner of configure.Push strut 61 include with The facing front end face 61a of inclined plate 40 (acting surface 42), along the axis of push strut 61 side opposite with front end face 61a after End face (end face) 61b and side 61c for connecting front end face 61a and rear end face 61b.In the example of diagram, front end face 61a Spherical shape.Even if as a result, as the variation of the deflection angle of inclined plate 40 formed by inclined plate 40 (acting surface 42) and push strut 61 Angle changes, and the pushing force for inclined plate 40 can also suitably transmitted from front end face 61a to acting surface 42.In addition, The rear end face 61b of push strut 61 has the flat surface with the axis vertical take-off of push strut 61.In addition, as long as rear end face 61b has energy The configuration and shape enough functioned as the acting surface of pressure supply power effect, specifically configuration and shape do not limit especially It is fixed.Here, " rear end face " refers to the face towards the side substantially opposite with " front end face ".Thus, it is also possible to rear end face 61b It is not necessarily the face of the rearmost end positioned at push strut 61.For example, rear end face 61b can also be set to the axis along push strut 61 Middle part.Also, rear end face 61b both can have the inclined flat surface of axis relative to push strut 61, can also contain Curved surface.For example, rear end face 61b can be from the dome shape outstanding of push strut 61, the dome shape being recessed towards push strut 61, wave Shape, the shape for being composed multiple flat surfaces make shape made of multiple surface compositions, form flat surface and surface composition Shape, the shape containing stage portion etc..

It is equipped with the 1st guide portion 23 for guiding the side 61c of push strut 61 in the 1st outer housing 21 (shell 20), is pushed Bar 61 is configured as moving freely relative to the 1st guide portion 23.Therefore, push strut 61 is maintained as part of it in the 1st guidance It is moved freely in portion 23.1st guide portion 23 is made of the through hole for being set to the 1st outer housing 21, has the section with push strut 61 Shape is in the cross sectional shape of complementary shape.That is, the 1st guide portion 23 is made of the cylindric through hole with circular cross-section.In In Fig. 1 and example shown in Fig. 2, the 1st guide portion 23 is integrally provided with the 1st outer housing 21 (shell 20).If by the 1st guide portion 23 It is integrally provided with the 1st outer housing 21, then the 1st guide portion 23 can be formed and perforating on the 1st outer housing 21, Neng Goutong It crosses simple processing and forms the 1st guide portion 23.Also, component is added in order to which the 1st guide portion 23 is arranged due to not needing, Help to cut down the components number of hydraulic pump 10 and reduces cost.In addition, the structure of the 1st guide portion 23 is not limited to This.It as an example, can also be by for example cylindric, using component being formed 1st guide portion 23 seperated with the 1st outer housing 21 It is installed on shell 20.

The recess portion 29 being connected to the 1st guide portion 23 is formed in the 1st outer housing 21 (shell 20).Recess portion 29 is for (not shown) The lid component insertion, utilizes the The lid component confining pressure room 65.As an example, it can be used and remember in Japanese JP2018-003609A The pushing pin unit of load is as The lid component.In this case, recess portion 29 is embedded in for the protrusion of pushing pin unit.

When pushing inclined plate 40 using push strut 61, there is a situation where such: in the work of the reaction force from inclined plate 40 Under, the power of the inclined direction of axis direction relative to push strut 61 acts on push strut 61.The hydraulic pump of present embodiment 10 have above-mentioned 1st guide portion 23, push away even if acting on as a result, relative to the power of the inclined direction of axis direction of push strut 61 The 61, the 1st guide portion 23 of compression bar also can suitably keep push strut 61, therefore push strut 61 can be made steadily to act.In addition, A part supply of the oil in shell 20 is maintained between the side 61c and the 1st guide portion 23 of push strut 61, thus carries out side Lubrication between face 61c and the 1st guide portion 23.

Pressure chamber 65 is formed in the side opposite with inclined plate 40 of push strut 61.In the present embodiment, it is located at and pushes Space between the rear end face 61b and The lid component of bar 61 becomes pressure chamber 65.The pressure input pressure room 65 of oil, pressure effect In the rear end face 61b of push strut 61.In particular, in the present embodiment, pressure directly acts on the rear end face of push strut 61 61b.Here, " directly effect " is the rear end face 61b that finger pressure does not act on push strut 61 across other components.In addition, simultaneously It is not limited to this, with being also possible to the force pin that pressure is recorded in other components, such as Japan JP2018-003609A Act on push strut 61.

In addition, in fig. 1 and fig. 2, the axis Ac for becoming the deflection center of inclined plate 40 prolongs along the direction orthogonal with paper It stretches.Thus, from being carried out from the direction orthogonal with both axis Ax and axis Ac (Fig. 1 and Fig. 2 in above or below) When, axis Ax and axis Ac extend orthogonally with respect to one another.In the example of diagram, axis Ac is located relative to for axis Ax to the 1st The position that 50 side of push part is offset by.As a result, coaxial line Ac intersect with axis Ax extend (axis Ac and axis Ax share one Point) the case where compare, can make the 2nd push part 60 minimize.

Then, it is illustrated referring to an example of Fig. 3 A and Fig. 3 B to the pressure for being input to the 2nd push part 60.In diagram In example, the pressure (being externally supplied the pressure come) for being input to the 2nd push part 60 is and inverted flux control pressure P_NIt is corresponding Pressure.In addition, the part for being labeled with appended drawing reference A, B in Fig. 3 A~Fig. 8 B is labeled with attached drawing with Fig. 1 and Fig. 2 respectively Mark the part connection of A, B.

In the case where hydraulic actuator stops (non-action) or slowly acts (fine motion work), the oil of hydraulic actuator Consumption is very small, is largely discharged to tank by the oil that hydraulic pump 10 sprays.At this point, for driving the engine of hydraulic pump 10 Etc. driving sources also consume fuel.Thus, in hydraulic actuator non-action or when fine motion is made, reduce the oil sprayed by hydraulic pump 10 Amount, and cut down be advantageous by the fuel that driving source consumes.

In inverted flux control (negative control) mechanism, route is being bypassed towards the center of tank from hydraulic pump via control valve , throttle orifice is equipped between control valve and tank.Also, detect the oily leakage flow across the throttle orifice and as throttle orifice Back pressure, the back pressure detected be inverted flux control pressure P_N.If in order to which the non-action of hydraulic actuator or fine motion are made and grasping Make control valve to reduce the flow of the oil gone via the control valve towards hydraulic actuator, then from liquid in inverted flux control mechanism The flow for the oil that press pump 10 is returned via center bypass route to tank increases.It is accompanied by this, the throttle orifice that center bypasses route is close Pressure (back pressure) P of preceding oil_NIncrease.

In the example shown in Fig. 3 A and Fig. 3 B, inverted flux control pressure P_NIt is converted into and pressure P_NCorresponding pressure Input pressure room 65.In particular, in the example of diagram, by pressure P_NPressure height it is reverse after pressure as with pressure P_N Corresponding pressure input pressure room 65.Here, with pressure P_NCorresponding pressure refers to based on pressure P_NThe pressure of generation.In In the example of diagram, using reversal valve 81 by pressure P_NIt is converted into and pressure P_NCorresponding pressure.Reversal valve 81 have valve rod and For pushing the spring of valve rod, by by pressure P_NReversal valve 81 is inputted, to control the position of the valve rod of reversal valve 81, is switched Oil circuit in reversal valve 81.

In biggish pressure P_NIn the case where inputting reversal valve 81, i.e., in the center bypass via inverted flux control mechanism In the case that the flow for the oil that line is discharged to tank is more, the valve rod of reversal valve 81 is due to pressure P_NAnd overcome the pushing force of spring simultaneously It is mobile, as shown in Figure 3A, from pioneer pump (パ イ ロ ッ ト Port Application プ) 71 towards the flow path 91 of the oil of reversal valve 81 not with self-commutation The flow path 92 of valve 81 towards the oil of the 2nd push part 60 is connected to.In the example of diagram, at this point, flow path 92 and 81 court of self-commutation valve It is connected to the flow path 93 of tank 73.In this case, the pressure of the oil sprayed by pioneer pump 71 does not input 60 (pressure of the 2nd push part Power room 65).Thus, as shown in Figure 1, push strut 61 does not push inclined plate 40, the deflection angle of inclined plate 40 becomes smaller.As a result, by hydraulic pump The flow of 10 oil sprayed is reduced.

In lesser pressure P_NIn the case where inputting reversal valve 81, i.e., in the center bypass via inverted flux control mechanism In the case that the flow for the oil that line is discharged to tank is less, the valve rod of reversal valve 81 due to spring pushing force and move, such as Fig. 3 B Shown, flow path 91 is connected to flow path 92.In the example of diagram, at this point, flow path 92 is not with self-commutation valve 81 towards the flow path of tank 73 93 connections.In this case, the pressure of the oil sprayed by pioneer pump 71 inputs the 2nd push part 60 (pressure chamber 65).Thus, such as Shown in Fig. 2, push strut 61 pushes inclined plate 40, and the deflection angle of inclined plate 40 becomes larger.The flow of the oil sprayed as a result, by hydraulic pump 10 increases Greatly.

In addition, the valve rod of reversal valve 81 is blocked in flow path 91 and 92 full communicating position (fully open position) of flow path and completely Position (full close position) between continuously move, additionally it is possible to the middle position between fully open position and full close position.That is, The aperture of the flow path of the connection flow path 91 and flow path 92 of reversal valve 81 is according to the pressure P for inputting the reversal valve 81 as a result,_NPressure Continuously control.

In the example shown in Fig. 3 A and Fig. 3 B, is sprayed by pioneer pump 71 and passed through using pressure P_NThe reversal valve 81 of control is adjusted The pressure that the 2nd push part 60 is inputted after the whole pressure becomes and pressure P_NCorresponding pressure.In particular, in the example of diagram In, in the pressure P of input reversal valve 81_NWhen becoming larger, the pressure of the 2nd push part 60 of input becomes smaller, in input reversal valve 81 Pressure P_NWhen becoming smaller, the pressure of the 2nd push part 60 of input becomes larger.That is, relative to pressure P_NPressure for, have pressure P_NPressure height it is reverse after the pressure of pressure input the 2nd push part 60.

In the case where the driving sources such as engine stop not spraying oil from hydraulic pump 10, reversal valve 81, which is not entered, to be come from The pressure P of inverted flux control mechanism_N.As a result, as shown in Figure 3B, flow path 91 is connected to flow path 92.On the other hand, stop in driving source In the case where only, pioneer pump 71 also stops, and does not spray oil from pioneer pump 71.Thus, in this case, the 2nd push part 60 does not have It is entered pressure.That is, the deflection angle of inclined plate 40 becomes smaller as shown in Figure 1, push strut 61 does not push inclined plate 40.In particular, inclined plate 40 Deflection angle become minimum.

In the case where previous hydraulic pump, in engine start, control is not entered pressure, therefore inclined plate with piston Deflection angle it is maximum.That is, torque required for driving hydraulic pump is maximum.In this case, start liquid to start engine The driving of press pump needs biggish driving force.In particular, oily viscosity becomes larger at low ambient temperatures, therefore start engine institute The driving torque needed becomes very large.Therefore, the case where using at low ambient temperatures for hydraulic pump needs increase to be used for The processing such as the size of battery of dynamic engine.

In contrast, shown in FIG. 1 to FIG. 3 B in the case where hydraulic pump 10, when the driving sources such as engine start, tiltedly The deflection angle of plate 40 is smaller.That is, torque required for driving hydraulic pump 10 is smaller.In particular, in the example of diagram, in engine Etc. driving sources when starting, the deflection angle of inclined plate 40 is minimum.That is, torque required for driving hydraulic pump 10 is minimum.Thus, even if Under the low temperature environment that the viscosity of oil becomes larger, driving torque required for the driving for starting hydraulic pump 10 also can reduce.As a result, can Enough reduce the size for starting the battery of driving source.This additionally aids the fluid power system including hydraulic pump 10 and driving source Whole miniaturization.In addition, the deflection angle of the inclined plate 40 when driving source starts is without that must be the smallest deflection angle.As long as driving The deflection angle of inclined plate 40 when dynamic source starts is the angle smaller than maximum deflection angle, it will be able to reduce driving 10 institute of hydraulic pump The torque needed.For example, driving source start when inclined plate 40 deflection angle can be set as than the smallest deflection angle with it is maximum The small angle of the angle in the center between deflection angle.In other words, the deflection angle of the inclined plate 40 when driving source starts can be set as Than 1/2 small angle of the sum of the smallest deflection angle and maximum deflection angle.

The hydraulic pump 10 of present embodiment includes: cylinder body 30, with multiple cylinder holes 32, and is configured to rotate； Piston 38 is movably maintained in each cylinder holes 32；Inclined plate 40 controls the shifting of piston 38 according to the size of deflection angle Momentum；1st push part 50, the direction for being used to become smaller towards the deflection angle of inclined plate 40 push inclined plate 40；And the 2nd pressing portion Part 60 is used to push inclined plate towards the direction that the deflection angle of inclined plate 40 becomes larger under the action of being externally supplied the pressure come 40。

According to such hydraulic pump 10, using be externally supplied come pressure come the 2nd push part 60 that controls towards oblique The direction that the deflection angle of plate 40 becomes larger pushes inclined plate 40, therefore can be in the driving that the pressure is not inputted to the 2nd push part 60 When source starts, reduce the deflection angle of inclined plate 40.Even if also can reduce out under the low temperature environment that the viscosity of oil becomes larger as a result, Driving torque required for the driving of beginning hydraulic pump 10.

In the hydraulic pump 10 of present embodiment, the 2nd push part 60 has for becoming larger towards the deflection angle of inclined plate 40 Direction push the push strut 61 of inclined plate 40, be externally supplied the pressure come and act on one opposite with inclined plate 40 of push strut 61 The end face 61b of side.

, can be by comparing simple the 2nd push part 60 of constitution realization according to such hydraulic pump 10, therefore can cut Subtract components number and realizes the miniaturization of hydraulic pump 10.

In the hydraulic pump 10 of present embodiment, being externally supplied the pressure come is and inverted flux control pressure P_NIt is corresponding Pressure.

According to such hydraulic pump 10, in hydraulic actuator non-action and when fine motion is made, the pushing of the 2nd push part 60 Power is reduced.Thus, inclined plate 40 deflects in such a way that its deflection angle becomes smaller, and the flow of the oil sprayed by hydraulic pump 10 is reduced.As a result, The waste of the fuel of driving source consumption can be cut down, and effectively improves the energy saving of the hydraulic device including hydraulic pump 10.

In addition, various changes can be implemented to above embodiment.Hereinafter, suitably illustrating on one side referring to attached drawing on one side Variation.In the attached drawing used in the following description and the following description, to can be constituted in the same manner as above embodiment Part use with the identical appended drawing reference of appended drawing reference used in the corresponding part in above embodiment, and omit weight Multiple explanation.

Fig. 4 A and Fig. 4 B are the figures for indicating a variation of hydraulic pump 10, and be for illustrating to be input to hydraulic pump 10 The figure of the pressure of 2 push part 60.In the example of diagram, the pressure for being input to the 2nd push part 60 (is externally supplied the pressure come Power) be and load-transducing (LS) flow control pressure P_LSCorresponding pressure.

In the example of diagram, from connection hydraulic pump 10 and control valve 75 flow path 94 branched halfway go out flow path 95 with change It is connected to valve 82.The oil being discharged due to the operating of hydraulic pump 10 from the cylinder holes 32 of hydraulic pump 10 is via flow path 94 towards control valve 75 It goes, and is gone from control valve 75 towards each hydraulic actuator.A part warp of the oil of (discharge) is sprayed by hydraulic pump 10 (cylinder holes 32) It is gone by the flow path 95 branched out from flow path 94 towards reversal valve 82.Also, reversal valve 82 is controlled with input load sensing flow rate Pressure P_LSThe opposite side in end end (being in figs. 4 a and 4b lower end, be also referred to as " opposite side end " below) with The flow path 96 gone out from the branched halfway of flow path 94 connects.It is as a result, from the discharge of the cylinder holes 32 of hydraulic pump 10 and defeated via flow path 94,96 The pressure of the oil entered acts on the opposite side end of reversal valve 82.

In load-transducing flow control mechanism, in the hydraulic actuator consumption compared with the oil mass sprayed by hydraulic pump 10 In the case that oil mass is less, as shown in Figure 4 A, reversal valve 82 is entered relatively small load-transducing flow control pressure P_LS.In In example shown in Fig. 4 A and Fig. 4 B, pressure P_LSIt is converted into and pressure P_LSCorresponding pressure input pressure room 65.Especially It is, in the example of diagram, with pressure P_LSPressure the corresponding pressure of height as with pressure P_LSCorresponding pressure input Pressure chamber 65.

Relatively small pressure P is entered in reversal valve 82_LSIn the case where, due to acting on the opposite side of reversal valve 82 The pressure of the oil in portion, the valve rod of reversal valve 82 overcome pressure P_LSAnd spring pushing force and move, as shown in Figure 4 A, from cylinder holes 32 It is not connected to towards the flow path 95 of the oil of reversal valve 82 with the flow path 92 of self-commutation valve 82 towards the oil of the 2nd push part 60.Scheming In the example shown, at this point, flow path 92 is connected to the flow path 93 of self-commutation valve 82 towards tank 73.In this case, from hydraulic pump 10 The pressure of the discharge of cylinder holes 32 and a part of oil in the oil gone towards control valve 75 does not input the 2nd push part 60.Thus, such as scheme Shown in 1, push strut 61 does not push inclined plate 40, and the deflection angle of inclined plate 40 becomes smaller.The flow of the oil sprayed as a result, by hydraulic pump 10 subtracts It is few.

Relatively large pressure P is entered in reversal valve 82_LSIn the case where, in pressure P_LSAnd the work of the pushing force of spring Under, the valve rod of reversal valve 82 overcomes the pressure of the oil for the opposite side end for acting on reversal valve 82 and moves, as shown in Figure 4 B, Flow path 95 is connected to flow path 92.In the example of diagram, at this point, flow path 93 of the flow path 92 not with self-commutation valve 82 towards tank 73 connects It is logical.In this case, defeated from the pressure of a part of oil in the oil that the cylinder holes 32 of hydraulic pump 10 is discharged and goes towards control valve 75 Enter the 2nd push part 60.Thus, as shown in Fig. 2, push strut 61 pushes inclined plate 40, the deflection angle of inclined plate 40 becomes larger.As a result, by The flow for the oil that hydraulic pump 10 sprays increases.

The driving sources such as engine stop and from hydraulic pump 10 (cylinder holes 32) do not spray (discharge) oil in the case where, no matter How is the position of the valve rod of reversal valve 82, all will not be from flow path 95 to 92 input pressure of flow path.That is, the 2nd push part 60 not by Input pressure.In this case, as shown in Figure 1, push strut 61 does not push inclined plate 40, the deflection angle of inclined plate 40 becomes smaller.In particular, The deflection angle of inclined plate 40 becomes minimum.

Fig. 5 A and Fig. 5 B are the figures for indicating another variation of hydraulic pump 10, and are for illustrating to be input to hydraulic pump 10 The figure of the pressure of 2nd push part 60.

There are such situations: being provided in hydraulic devices such as Work machines while locking the dynamic of multiple hydraulic actuators The locking level of work.In the example of diagram, the pressure (being externally supplied the pressure come) for being input to the 2nd push part 60 is and passes through The operation of the locking level and the locking rod pressure P generated_LLCorresponding pressure.

In the example shown in Fig. 5 A and Fig. 5 B, rod pressure P is locked_LLIt is converted into and pressure P_LLCorresponding pressure is defeated Enter pressure chamber 65.In particular, in the example of diagram, by pressure P_LLPressure height it is reverse after pressure as with pressure P_LL Corresponding pressure input pressure room 65.In the example of diagram, using reversal valve 83 by pressure P_LLIt is converted into and pressure P_LLPhase Corresponding pressure.Reversal valve 83 has valve rod and the spring for pushing valve rod, by by pressure P_LLReversal valve 83 is inputted, thus The position of the valve rod of reversal valve 83 is controlled, the oil circuit in reversal valve 83 is switched.

In the movement using locking rod lock hydraulic actuator, and reversal valve 83 is entered lesser pressure P_LLThe case where Under, the valve rod of reversal valve 83 is pushed and positioned by spring, as shown in Figure 5A, from pioneer pump 71 towards the stream of the oil of reversal valve 83 Road 91 is not connected to the flow path 92 of self-commutation valve 83 towards the oil of the 2nd push part 60.In the example of diagram, at this point, flow path 92 It is connected to the flow path 93 of self-commutation valve 83 towards tank 73.In this case, the pressure of the oil sprayed by pioneer pump 71 does not input the 2nd Push part 60 (pressure chamber 65).Thus, as shown in Figure 1, push strut 61 does not push inclined plate 40, the deflection angle of inclined plate 40 becomes smaller. The flow of the oil sprayed as a result, by hydraulic pump 10 is reduced.

It is released from using locking of the locking level to the movement of hydraulic actuator, and reversal valve 83 is entered biggish pressure P_LLIn the case where, the valve rod of reversal valve 83 is in pressure P_LLUnder the action of overcome the pushing force of spring and move, as shown in Figure 5 B, Flow path 91 is connected to flow path 92.In the example of diagram, at this point, flow path 93 of the flow path 92 not with self-commutation valve 83 towards tank 73 connects It is logical.In this case, the pressure of the oil sprayed by pioneer pump 71 inputs the 2nd push part 60 (pressure chamber 65).Thus, such as Fig. 2 Shown, push strut 61 pushes inclined plate 40, and the deflection angle of inclined plate 40 becomes larger.The flow of the oil sprayed as a result, by hydraulic pump 10 increases.

Fig. 6 A~Fig. 6 C is the figure for indicating another variation of hydraulic pump 10, and is for illustrating to be input to hydraulic pump 10 The figure of the pressure of 2nd push part 60.In the example of diagram, the pressure for being input to the 2nd push part 60 is and inverted flux control Pressure P_NAnd locking rod pressure P_LLCorresponding pressure.

It is less in the flow for the oil that the center bypass route via inverted flux control mechanism is discharged to tank, and utilize locking level In the case where the movement for having locked hydraulic actuator, that is, be entered lesser pressure P in reversal valve 81_N, and reversal valve 83 also by Input lesser pressure P_LLIn the case where, the valve rod of reversal valve 81,83 is pushed and positioned by spring, as shown in Figure 6A, from first The flow path 91 for leading pump 71 towards the oil of reversal valve 83 is not connected to the flow path 97 of self-commutation valve 83 towards the oil of reversal valve 81.Separately Outside, the flow path 92 of self-commutation valve 83 towards the oil of the 2nd push part 60 is connected to flow path 97 via reversal valve 81.In the example of diagram In, at this point, flow path 97 is connected to the flow path 93 of self-commutation valve 83 towards tank 73.Also, flow path 92 not with 81 direction of self-commutation valve The flow path 98 of tank 73 is connected to.In this case, the pressure of the oil sprayed by pioneer pump 71 does not input the 2nd push part 60.Thus, As shown in Figure 1, push strut 61 does not push inclined plate 40, the deflection angle of inclined plate 40 becomes smaller.The stream of the oil sprayed as a result, by hydraulic pump 10 Amount is reduced.

It is released from using locking of the locking level to the movement of hydraulic actuator, and reversal valve 83 is entered biggish pressure P_LLWhen, the valve rod of reversal valve 83 is in pressure P_LLUnder the action of overcome the pushing force of spring and move, as shown in Figure 6B, flow path 91 It is connected to flow path 97.In the example of diagram, at this point, flow path 97 is not connected to flow path 93.In this case, it is sprayed by pioneer pump 71 Oil pressure via flow path 91,97,92 input the 2nd push part 60.Thus, as shown in Fig. 2, push strut 61 pushes inclined plate 40, the deflection angle of inclined plate 40 becomes larger.The flow of the oil sprayed as a result, by hydraulic pump 10 increases.

Increase in the flow for the oil that the center bypass route via inverted flux control mechanism is discharged to tank, and 81 quilt of reversal valve Input biggish pressure P_NWhen, the valve rod of reversal valve 81 is in pressure P_NUnder the action of overcome the pushing force of spring and move, such as Fig. 6 C Shown, flow path 97 is not connected to flow path 92.In the example of diagram, at this point, flow path 92 is connected to flow path 98.In this case, by The pressure for the oil that pioneer pump 71 sprays does not input the 2nd push part 60.Thus, as shown in Figure 1, push strut 61 does not push inclined plate 40, the deflection angle of inclined plate 40 becomes smaller.The flow of the oil sprayed as a result, by hydraulic pump 10 is reduced.

Fig. 7 A and Fig. 7 B are the figures for indicating another variation of hydraulic pump 10, and are for illustrating to be input to hydraulic pump 10 The figure of the pressure of 2nd push part 60.In the example of diagram, the pressure for being input to the 2nd push part 60 (is externally supplied Pressure) be and load-transducing flow control pressure P_LSAnd locking rod pressure P_LLCorresponding pressure.In this variation, joining Utilization locking rod pressure P is configured with according to the midway of the flow path 95 of Fig. 4 A and Fig. 4 the B variation being illustrated_LLAnd what is acted changes To valve 83.The structure, movement and effect of each section in addition to reversal valve 83 of this variation are carried out with referring to Fig. 4 A and Fig. 4 B The variation of explanation is same, therefore omits specific description.

In the example shown in Fig. 7 A and Fig. 7 B, reversal valve 83 is configured in the midway of flow path 95, and flow path 95 is divided into as a result, It connects the flow path 95a of flow path 94 and reversal valve 83 and connects the flow path 95b of reversal valve 83 and reversal valve 82.

Using the movement of hydraulic actuator of locking rod lock, reversal valve 83 is entered lesser pressure P_LL.The valve rod of reversal valve 83 is pushed and positioned by spring, as shown in Figure 7 A, comes out from the branched halfway of flow path 94 and with commutation The flow path 95b connection that the flow path 95a that valve 83 connects is not connect with by reversal valve 83 and reversal valve 82.In the example of diagram, at this point, Flow path 95b is connected to the flow path 99 of self-commutation valve 83 towards tank 73.

In the example shown in Fig. 7 A, regardless of the position of the valve rod of reversal valve 82, flow path 94 not with self-commutation valve 82 It is connected to towards the flow path 92 of the oil of the 2nd push part 60.In the example of diagram, at this point, flow path 92 and self-commutation valve 82 are towards tank 73 flow path 93 is connected to.In this case, from one in the oil that the cylinder holes 32 of hydraulic pump 10 is discharged and goes towards control valve 75 The pressure of oil is divided not input the 2nd push part 60.Thus, as shown in Figure 1, push strut 61 does not push inclined plate 40, inclined plate 40 it is inclined Corner becomes smaller.The flow of the oil sprayed as a result, by hydraulic pump 10 is reduced.

It is released from using locking of the locking level to the movement of hydraulic actuator, and reversal valve 83 is entered biggish pressure P_LLWhen, the valve rod of reversal valve 83 is in pressure P_LLUnder the action of overcome the pushing force of spring and move, as shown in Figure 7 B, flow path 95a It is connected to flow path 95b via reversal valve 83.As a result, from the oil that the cylinder holes 32 of hydraulic pump 10 is discharged and goes towards control valve 75 The pressure of a part of oil reaches reversal valve 82 via flow path 95 (95a, 95b).

State, reversal valve 82 shown in Fig. 7 B valve rod due to pressure P_LSAnd when moving, flow path 95 (95b) and flow path 92 connections.In the example of diagram, at this point, flow path 92 is not connected to the flow path 93 of self-commutation valve 82 towards tank 73.In this case, The 2nd push part is inputted from the pressure of a part of oil in the oil that the cylinder holes 32 of hydraulic pump 10 is discharged and goes towards control valve 75 60.Thus, as shown in Fig. 2, push strut 61 pushes inclined plate 40, the deflection angle of inclined plate 40 becomes larger.It is sprayed as a result, by hydraulic pump 10 The flow of oil increases.

As another variation, the pressure for being also possible to be input to the 2nd push part 60 is and positive flow control (positive control System) pressure P_PCorresponding pressure.Pressure P_PBoth the pressure chamber 65 that the 2nd push part 60 can have been directly inputted, also can use and changes It is converted into and pressure P to valve etc._PCorresponding another pressure input pressure room 65.

Here, illustrating pressure P_PBe not converted into another pressure just directly input the pressure chamber 65 of the 2nd push part 60 Example.In positive flow control mechanism, the pilot pressure of the guide operating valve for being operated to valve feeds back to hydraulic pump 10. In this variation, the pilot pressure is as pressure P_PInput the 2nd push part 60 (pressure chamber 65).In the 2nd push part 60 It is entered lesser pressure P_PIn the case where, as shown in Figure 1, push strut 61 does not push inclined plate 40, the deflection angle of inclined plate 40 becomes smaller. The flow of the oil sprayed as a result, by hydraulic pump 10 is reduced.Biggish pressure P is entered in the 2nd push part 60_PIn the case where, As shown in Fig. 2, push strut 61 pushes inclined plate 40, the deflection angle of inclined plate 40 becomes larger.The flow of the oil sprayed as a result, by hydraulic pump 10 Increase.

Fig. 8 A and Fig. 8 B are the figures for indicating another variation of hydraulic pump 10, and are for illustrating to be input to hydraulic pump 10 The figure of the pressure of 2nd push part 60.In the example of diagram, the pressure for being input to the 2nd push part 60 (is externally supplied Pressure) be electric signal (voltage signal) V using electromagnetic proportional valve be converted into it is hydraulic obtained from pressure.

In the example of diagram, reversal valve 85 is electromagnetic proportional valve, and has the electric signal V of input being converted into corresponding liquid The function of the pressure of pressure.As electric signal V, be able to use for example with inverted flux control pressure P_N, positive flow control pressure P_P, it is negative It carries sensing flow rate and controls pressure P_LS, locking rod pressure P_LLAny one of corresponding electric signal or by the two in them Electric signal obtained from combination of the above.

In the case where reversal valve 85 is entered lesser electric signal V, the valve rod of reversal valve 85 utilizes the pushing force of spring Positioning, as shown in Figure 8 A, from pioneer pump 71 towards the flow path 91 of the oil of reversal valve 85 not with self-commutation valve 85 towards the 2nd pressing portion The flow path 92 of the oil of part 60 is connected to.In the example of diagram, at this point, the flow path 93 of flow path 92 and self-commutation valve 85 towards tank 73 connects It is logical.In this case, the pressure of the oil sprayed by pioneer pump 71 does not input the 2nd push part 60.Thus, as shown in Figure 1, pushing Bar 61 does not push inclined plate 40, and the deflection angle of inclined plate 40 becomes smaller.The flow of the oil sprayed as a result, by hydraulic pump 10 is reduced.

In the case where reversal valve 85 is entered biggish electric signal V, the valve rod of reversal valve 85 is driven according to electric signal V Overcome the pushing force of spring under the action of the pushing force that dynamic solenoid generates and move, as shown in Figure 8 B, flow path 91 and flow path 92 connections.In the example of diagram, at this point, flow path 92 is not connected to the flow path 93 of self-commutation valve 85 towards tank 73.In this case, The pressure of the oil sprayed by pioneer pump 71 inputs the 2nd push part 60.Thus, as shown in Fig. 2, push strut 61 pushes inclined plate 40, The deflection angle of inclined plate 40 becomes larger.The flow of the oil sprayed as a result, by hydraulic pump 10 increases.

The hydraulic pump 10 of each variation described above also liquid with referring to Fig.1~Fig. 3 B embodiment being illustrated Similarly, when the driving sources such as engine start, the deflection angle of inclined plate 40 is minimum for press pump 10.That is, required for driving hydraulic pump 10 Torque it is minimum.Thus, even if also can reduce the driving institute for starting hydraulic pump 10 under the low temperature environment that oily viscosity becomes larger The driving torque needed.

In addition, several variations of above embodiment are explained above, of course it is also possible to be appropriately combined multiple deformations Example is applied.