阅读说明：本技术 泵单元和施工机械 (Pump unit and construction machine ) 是由 赤见俊也 山口祥 于 2020-02-28 设计创作，主要内容包括：本发明提供一种泵单元和施工机械。本发明的泵单元具备：第1泵,其具有：第1壳体；旋转轴,其以可旋转的方式设置于所述第1壳体；壁面部,其位于所述旋转轴的轴线上且位于所述第1壳体的一侧；第1吸入部和第1排出部,其形成于所述第1壳体的所述壁面部；凸部,其设置于所述第1吸入部和所述第1排出部中的至少任一者的内侧面部；以及固定用孔部,其从所述壁面部的外表面朝向所述凸部地形成；和第2泵,其通过将固定构件安装于所述固定用孔部而固定于所述壁面部的所述外表面。(The invention provides a pump unit and a construction machine. The pump unit of the present invention includes: a 1 st pump having: 1, a first shell; a rotating shaft rotatably provided to the 1 st housing; a wall surface portion located on an axis of the rotation shaft and located on one side of the 1 st housing; a 1 st suction part and a 1 st discharge part formed on the wall surface part of the 1 st housing; a convex portion provided on an inner side surface portion of at least one of the 1 st suction portion and the 1 st discharge portion; and a fixing hole formed from an outer surface of the wall surface portion toward the convex portion; and a 2 nd pump fixed to the outer surface of the wall surface portion by attaching a fixing member to the fixing hole portion.)

1. A pump unit is provided with:

a 1 st pump having: 1, a first shell; a rotating shaft rotatably provided in the 1 st housing; a wall surface portion located on an axis of the rotation shaft and located on one side of the 1 st housing; a 1 st suction part and a 1 st discharge part formed on the wall surface part of the 1 st housing; a convex portion provided on an inner side surface portion of at least one of the 1 st suction portion and the 1 st discharge portion; and a fixing hole formed from an outer surface of the wall surface portion toward the convex portion; and

and a 2 nd pump fixed to the outer surface of the wall surface portion by attaching a fixing member to the fixing hole portion.

2. The pump unit of claim 1,

the convex portion is disposed at the center in the width direction orthogonal to the flow direction of the fluid flowing through the 1 st suction portion and the 1 st discharge portion.

3. Pump unit according to claim 1 or 2,

the 2 nd pump includes:

a 2 nd housing;

a 2 nd suction unit formed on a 1 st wall surface portion of the 2 nd casing and configured to suck liquid into the 2 nd casing; and

a 2 nd discharge portion formed on a 2 nd wall surface portion of the 2 nd casing for discharging liquid to the outside of the 2 nd casing,

a side surface portion of the 1 st casing in which the discharge port portion of the 1 st discharge portion is formed faces the 2 nd wall surface portion of the 2 nd casing in the same direction.

4. The pump unit of claim 3,

the 1 st suction part of the 1 st pump communicates with the 2 nd suction part of the 2 nd pump.

5. Pump unit according to claim 1 or 2,

the convex portion becomes tapered as going toward the projecting direction.

6. Pump unit according to claim 1 or 2,

the convex part is an elliptical cone, and the convex part is an elliptical cone,

the long axis of the projection is along the flow direction of the fluid flowing through the 1 st suction part and the 1 st discharge part.

7. The pump unit of claim 5,

the convex part is an elliptical cone, and the convex part is an elliptical cone,

the long axis of the projection is along the flow direction of the fluid flowing through the 1 st suction part and the 1 st discharge part.

8. A pump unit is provided with:

a 1 st pump having: 1, a first shell; a rotating shaft rotatably provided in the 1 st housing; a wall surface portion located on an axis of the rotation shaft and located on one side of the 1 st housing; a 1 st suction part and a 1 st discharge part formed on the wall surface part of the 1 st housing; a convex portion that is provided on an inner side surface portion of at least one of the 1 st suction portion and the 1 st discharge portion and is provided at a center in a width direction orthogonal to a flow direction of the fluid flowing in the 1 st suction portion and the 1 st discharge portion, the convex portion being an elliptical cone having a major axis along the flow direction of the fluid flowing in the 1 st suction portion and the 1 st discharge portion, and the convex portion becoming tapered as going toward a projecting direction; and a fixing hole formed from an outer surface of the wall surface portion toward the convex portion; and

a 2 nd pump having: a 2 nd housing; a 2 nd suction part formed on a 1 st wall surface part and communicated with the 1 st suction part of the 1 st pump; and a 2 nd discharge portion formed in a 2 nd wall surface portion of the 2 nd casing facing in the same direction as a side surface portion of the 1 st casing in which the discharge port portion of the 1 st discharge portion is formed, the 2 nd pump being fixed to the outer surface of the wall surface portion by attaching a fixing member to the fixing hole portion.

9. A construction machine is provided with:

a pump unit as claimed in any one of claims 1 to 8; and

a vehicle body on which the pump unit is mounted.

Technical Field

The invention relates to a pump unit and a construction machine.

Background

As a hydraulic pump unit mounted on a construction machine such as a hydraulic excavator, a pump unit including two types of pumps, a main pump and a gear pump, is known.

The main pump has a rotary shaft supported to be rotatable in a pump housing, for example. A cylinder is fitted and fixed to the outer peripheral surface of the rotating shaft. The rotary shaft and the cylinder block rotate integrally. The cylinder block is provided with a plurality of cylinder bores. A piston is inserted into each cylinder bore. Then, the cylinder bore and the piston constitute a cylinder chamber.

A suction path and a discharge path through which the working oil flows are formed in the bottom of the portion of the pump housing forming the cylinder chamber. Further, a swash plate supported to be rotatable with respect to the pump housing is provided at an end portion of the piston opposite to the end portion of the portion where the cylinder chamber is formed.

With this structure, the pistons slide along the swash plate, and displacement of the pistons in the cylinder bores is restricted by the swash plate. When the piston slides along the swash plate, the piston slides in the cylinder hole. Thereby, the volume of the cylinder chamber changes. When the cylinder chamber expands, the working oil is sucked from the outside of the pump housing to the cylinder chamber through the suction path. When the cylinder chamber contracts, the working oil in the cylinder chamber is discharged to the outside of the pump housing through the discharge passage.

On the other hand, the gear pump includes a gear housing and two gears housed in the gear housing. The working oil is sucked or discharged by rotating the two gears that mesh with each other.

Disclosure of Invention

Problems to be solved by the invention

However, when the pump unit is to be downsized, it is conceivable to integrate the main pump and the gear pump.

In addition, in order to improve the driving efficiency of the pump unit, it is conceivable to couple the rotary shaft of the main pump and the gear of the gear pump. With this configuration, the gear pump can be driven by the rotation of the rotary shaft in the main pump.

In order to achieve the above-described reduction in size and improvement in drive efficiency, it is preferable to arrange the gear pump coaxially with the rotation shaft of the main pump and integrate them. However, in the case where the gear pump is thus configured, it is necessary to fasten, for example, bolts for fixing the gear pump to the bottom of the pump housing. Since the suction path and the discharge path are formed in the pump housing, the female screw portion for fastening the bolt penetrates the suction path or the discharge path on the outside of the pump housing. Therefore, there is a possibility that the main pump may not operate normally.

It is also conceivable to increase the thickness of the bottom of the pump housing so that the suction path or the discharge path does not penetrate the outside of the pump housing even if a female screw portion is formed in the bottom of the pump housing. However, if the bottom of the pump housing is thickened, the axial length of the pump unit becomes long.

The invention provides a pump unit and a construction machine, which can reliably realize miniaturization and high efficiency of driving efficiency.

Means for solving the problems

A pump unit according to an aspect of the present invention includes: a 1 st pump having: 1, a first shell; a rotating shaft rotatably provided in the 1 st housing; a wall surface portion located on an axis of the rotation shaft and located on one side of the 1 st housing; a 1 st suction part and a 1 st discharge part formed on the wall surface part of the 1 st housing; a convex portion provided on an inner side surface portion of at least one of the 1 st suction portion and the 1 st discharge portion; and a fixing hole formed from an outer surface of the wall surface portion toward the convex portion; and a 2 nd pump fixed to the outer surface of the wall surface portion by attaching a fixing member to the fixing hole portion.

With this configuration, even if the fixing hole is formed in the wall surface portion of the pump housing in which the 1 st suction portion and the 1 st discharge portion are formed, the outside of the pump housing can be prevented from penetrating the 1 st suction portion or the 1 st discharge portion through the fixing hole without increasing the thickness of the wall surface portion. Therefore, the axial length of the pump unit can be suppressed from increasing, and the pump unit can be downsized. Further, since the 2 nd pump (gear pump) can be disposed on the wall surface portion of the 1 st pump located on the axis of the rotary shaft, the rotational force of the rotary shaft in the 1 st pump can be easily transmitted to the housing (gear housing) of the 2 nd pump. Therefore, the driving efficiency of the pump unit can be improved.

In the above configuration, the convex portion may be disposed at a center in a width direction orthogonal to a flow direction of the fluid flowing through the 1 st suction portion and the 1 st discharge portion.

With this configuration, it is possible to suppress a large difference in flow rate between the right side and the left side of the liquid around the convex portion in the direction perpendicular to the flow of the liquid. Therefore, the disturbance of the flow of the liquid in the 1 st suction unit and the 1 st discharge unit can be suppressed to the minimum, and the flow of the liquid can be stabilized.

Therefore, the driving efficiency of the pump unit can be further improved.

In the above configuration, the 2 nd pump may include: a 2 nd housing; a 2 nd suction unit formed on a 1 st wall surface portion of the 2 nd casing and configured to suck liquid into the 2 nd casing; and a 2 nd discharge portion formed in a 2 nd wall surface portion of the 2 nd casing for discharging liquid out of the 2 nd casing, a side surface portion of the 1 st casing in which a discharge port portion of the 1 st discharge portion is formed facing in the same direction as the 2 nd wall surface portion of the 2 nd casing.

With this configuration, the 1 st discharge port of the 1 st pump is disposed adjacent to the 2 nd discharge port of the 2 nd discharge portion of the 2 nd pump. Therefore, the work of connecting the pipes to the respective discharge portions and the work of routing the pipes can be easily performed.

In the above configuration, the 1 st suction part of the 1 st pump may communicate with the 2 nd suction part of the 2 nd pump.

With this configuration, the liquid can be guided to the 2 nd suction unit of the 2 nd pump through the 1 st suction unit of the 1 st pump. Therefore, the structure of each suction portion can be simplified, and the pump unit can be further downsized.

In the above configuration, the convex portion may be tapered as it goes toward the projecting direction.

With this configuration, the flow path resistance to the liquid by the convex portion can be reduced as much as possible. Therefore, the disturbance of the flow of the liquid in the 1 st suction unit and the 1 st discharge unit can be suppressed as much as possible. Therefore, the driving efficiency of the pump unit can be further improved.

In the above configuration, the convex portion may be an elliptical cone, and a long axis of the convex portion may be along a flow direction of the fluid flowing through the 1 st suction portion and the 1 st discharge portion.

With this configuration, the flow path resistance to the liquid by the convex portion can be reliably reduced. Therefore, the turbulence of the flow of the liquid in the 1 st suction unit and the 1 st discharge unit can be reliably suppressed. Therefore, the driving efficiency of the pump unit can be reliably improved.

A pump unit according to another aspect of the present invention includes: a 1 st pump having: 1, a first shell; a rotating shaft rotatably provided in the 1 st housing; a wall surface portion located on an axis of the rotation shaft and located on one side of the 1 st housing; a 1 st suction part and a 1 st discharge part formed on the wall surface part of the 1 st housing; a convex portion that is provided on an inner side surface portion of at least one of the 1 st suction portion and the 1 st discharge portion and is provided at a center in a width direction orthogonal to a flow direction of the fluid flowing in the 1 st suction portion and the 1 st discharge portion, the convex portion being an elliptical cone having a major axis along the flow direction of the fluid flowing in the 1 st suction portion and the 1 st discharge portion, and the convex portion becoming tapered as going toward a projecting direction; and a fixing hole formed from an outer surface of the wall surface portion toward the convex portion; and a 2 nd pump having: a 2 nd housing; a 2 nd suction part formed on a 1 st wall surface part and communicated with the 1 st suction part of the 1 st pump; and a 2 nd discharge portion formed in a 2 nd wall surface portion of the 2 nd casing facing in the same direction as a side surface portion of the 1 st casing in which the discharge port portion of the 1 st discharge portion is formed, the 2 nd pump being fixed to the outer surface of the wall surface portion by attaching a fixing member to the fixing hole portion.

With this configuration, the pump unit can be downsized and the driving efficiency can be improved.

A construction machine according to another aspect of the present invention includes the pump unit described above and a vehicle body on which the pump unit is mounted.

With this configuration, it is possible to provide a construction machine that can be reliably reduced in size and increased in driving efficiency.

ADVANTAGEOUS EFFECTS OF INVENTION

The pump unit and the construction machine can be reliably miniaturized and have high driving efficiency.

Drawings

Fig. 1 is a schematic configuration diagram of a construction machine according to an embodiment of the present invention.

Fig. 2 is a structural diagram of a pump unit in the embodiment of the present invention.

Fig. 3 is a side view seen from a in fig. 2.

Fig. 4 is a cross-sectional view of the convex portion in the axial direction in the modification of the embodiment of the present invention.

Fig. 5 is a sectional view taken along line B-B of fig. 4.

Description of the reference numerals

1. A main pump (1 st pump); 2. a main case (1 st case); 3. a rotating shaft; 100. a construction machine; 101. a revolving body (vehicle body); 102. a movable body (vehicle body); 110. a pump unit; 111. a gear pump (2 nd pump); 119. a bottom wall (wall surface portion); 119b, an outer surface; 119d, a 2 nd side surface (side surface portion); 122. a 1 st suction path (1 st suction unit); 122b, an inner side surface (inner side surface portion); 123. a 1 st discharge path (1 st discharge unit); 123a, an exhaust port (exhaust port portion); 126. a convex portion; 127. an internal thread portion (fixing hole portion); 141. a gear housing (2 nd housing); 141a, a wall surface (wall surface part 1); 141c, the 2 nd side wall surface (the 2 nd wall surface portion); 144. a 2 nd suction path (2 nd suction part); 147. a bolt (fixing member); 148. a 2 nd discharge path (2 nd discharge unit); C. a central axis (axis); J. a long axis.

Detailed Description

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

(construction machine)

Fig. 1 is a schematic configuration diagram of a construction machine 100.

As shown in fig. 1, the construction machine 100 is, for example, a hydraulic excavator. The construction machine 100 includes a revolving structure (corresponding to a vehicle body in claims) 101 and a moving body (corresponding to a vehicle body in claims) 102. The revolving unit 101 is provided on the moving body 102 so as to be revolvable. The rotator 101 is provided with a pump unit 110.

Rotator 101 includes: a cab 103 on which an operator can ride; a boom 104 having one end connected to the cab 103 so as to be swingable; an arm 105 having one end connected to the other end (distal end) of the boom 104 on the side opposite to the cab 103 so as to be swingable; and a bucket 106 connected to the other end (tip end) of the arm 105 on the opposite side to the arm 104 so as to be swingable. Further, the pump unit 110 is provided in the cab 103. The cab 103, the boom 104, the arm 105, and the bucket 106 are driven by the hydraulic oil supplied from the pump unit 110.

(Pump Unit)

Fig. 2 is a structural view of the pump unit 110. Fig. 3 is a side view seen from a in fig. 2.

The pump unit 110 is a so-called hydraulic pump that sucks and discharges hydraulic oil. As shown in fig. 2 and 3, the pump unit 110 has a structure in which a main pump (corresponding to the 1 st pump in the claims) 1 and a gear pump (corresponding to the 2 nd pump in the claims) 111 as an auxiliary pump are integrated. In fig. 2, only the main pump 1 is shown in a cross section along the axial direction.

(Main Pump)

The main pump 1 is a so-called swash plate type variable displacement hydraulic pump. The main pump 1 includes the following components as main components: a main housing (corresponding to the 1 st housing in claims) 2; a rotary shaft 3 supported to be rotatable with respect to the main casing 2; a cylinder 4 housed in the main casing 2 and fixed to the rotary shaft 3; and a swash plate 5 which is rotatably housed in the main casing 2 and controls the discharge amount of the hydraulic oil discharged from the main pump 1.

In fig. 2, the scale of each member is appropriately changed to make the description easy to understand.

In the following description, a direction parallel to the center axis C of the rotary shaft 3 is referred to as an axial direction, a rotation direction of the rotary shaft 3 is referred to as a circumferential direction, and a radial direction of the rotary shaft 3 is simply referred to as a radial direction.

The main casing 2 includes: a box-shaped case body 9 having an opening 9 a; and a front flange 10 for closing the opening 9a of the housing main body 9.

The case main body 9 has a bottom wall (corresponding to a wall surface portion in claims) 119 on a side opposite to the opening 9 a. The cylinder 4 is disposed on the inner surface 119a side of the bottom wall 119.

The gear pump 111 is attached to an outer surface 119b of the bottom wall 119.

Further, a rotation shaft insertion hole 121 through which the rotation shaft 3 can be inserted is formed in the bottom wall 119 so as to penetrate in the plate thickness direction of the bottom wall 119. A bearing 11 for rotatably supporting one end of the rotary shaft 3 is provided in the bottom wall 119 at a position close to the inner surface 119 a. That is, the bottom wall 119 is a wall surface of the housing main body 9 located on the center axis C of the rotary shaft 3.

Further, a 1 st suction path (corresponding to a 1 st suction portion in the claims) 122 and a 1 st discharge path (corresponding to a 1 st discharge portion in the claims) 123 are formed on both sides of the bottom wall 119 with the rotary shaft 3 interposed therebetween. The 1 st suction path 122 has a suction port 122a on the 1 st side 119c of the bottom wall 119. Suction port 122a is connected to a tank not shown. The 1 st suction path 122 extends in the bottom wall 119 so that an opening area becomes gradually smaller from the 1 st side surface 119c toward the rotation shaft 3.

A 1 st communication path 124 communicating the 1 st suction path 122 with the inner surface 119a of the bottom wall 119 is formed at an end portion of the 1 st suction path 122 on the rotary shaft 3 side. The 1 st communication path 124 communicates the 1 st suction path 122 with the supply port 19a of the valve plate 19 discussed later.

Further, a 2 nd communication path 125 communicating the 1 st suction path 122 with the outer surface 119b of the bottom wall 119 is formed at an end portion of the 1 st suction path 122 on the rotary shaft 3 side. The 2 nd communication path 125 communicates the 1 st suction path 122 with a 2 nd suction path (equivalent to the 2 nd suction portion in the claims) 144, which will be discussed later, of the gear pump 111.

Further, an O-ring groove 118 is formed on an outer surface 119b of the bottom wall 119 so as to surround the rotation shaft insertion hole 121 and the 2 nd communication path 125. An O-ring 117 is fixed to the O-ring groove 118. The O-ring seal 117 ensures sealing between the main housing 2 and a gear housing 141 of the gear pump 111, which will be discussed later.

With this configuration, the working oil is sucked into the 1 st suction path 122 through the suction port 122a from a tank not shown. The working oil sucked into the 1 st suction path 122 flows to the 1 st communication path 124 and the 2 nd communication path 125.

Here, a substantially cylindrical protrusion 126 protruding into the 1 st suction path 122 is provided on an inner surface (corresponding to an inner surface in the claims) 122b of the 1 st suction path 122. The projection 126 is disposed closer to the 2 nd communication path 125 than the center between the suction port 122a and the 2 nd communication path 125 and closer to the outer surface 119b side (gear pump 111 side) of the bottom wall 119. The convex portion 126 is disposed at the center in the width direction of the 1 st suction passage 122, which is orthogonal to the direction in which the hydraulic oil flows through the 1 st suction passage 122 (the vertical direction in fig. 2, the horizontal direction in fig. 3). The protrusion 126 is a portion for fixing the gear pump 111 to the bottom wall 119 of the housing main body 9.

A female screw portion (corresponding to a fixing hole portion in claims) 127 is formed in the bottom wall 119 in a section from the outer surface 119b to the inside of the convex portion 126.

The 1 st discharge path 123 includes a discharge port (corresponding to a discharge port portion in the claims) 123a on a 2 nd side surface (corresponding to a side surface portion in the claims) 119d of the bottom wall 119 located on the opposite side of the 1 st side surface 119c with respect to the rotation axis 3. The discharge port 123a is connected to the cab 103, the boom 104, the arm 105, and the bucket 106 via a control valve or the like, not shown. The 1 st discharge path 123 extends from the 2 nd side surface 119d toward the rotation axis 3 in the bottom wall 119.

A 3 rd communication path 128 for communicating the 1 st discharge path 123 with the inner surface 119a of the bottom wall 119 is formed at an end portion of the 1 st discharge path 123 on the rotary shaft 3 side. The 3 rd communication path 128 communicates the 1 st discharge path 123 and a non-illustrated discharge port of the valve plate 19 discussed later.

The front flange 10 is formed with a through hole 13 through which the rotary shaft 3 can pass. The through hole 13 is provided with a bearing 14 for rotatably supporting the other end side of the rotary shaft 3. Further, an oil seal 15 is provided in the through hole 13 at a position on the opposite side of the bearing 14 from the housing main body 9 (outside the front flange 10). Further, two attachment plates 137 for fixing the main pump 1 to the revolving unit 101 and the like are integrally formed with the front flange 10. The two mounting plates 137 are disposed on both sides with the rotating shaft 3 interposed therebetween. The mounting plate 137 extends toward the radially outer side.

The rotary shaft 3 is formed to have a step shape. The rotary shaft 3 has a structure in which the following components are coaxially arranged: a rotation shaft main body 131 disposed in the main casing 2; a 1 st bearing portion 132 integrally formed on the rotation shaft main body 131 on the side of the bottom wall 119 of the housing main body 9; a transmission shaft 133 integrally formed at an end of the 1 st bearing part 132 opposite to the rotation shaft main body 131; a 2 nd bearing 134 integrally formed at an end of the rotary shaft main body 131 on the front flange 10 side; and a coupling shaft 135 integrally formed at an end of the 2 nd bearing 134 opposite to the rotation shaft main body 131.

The 1 st bearing portion 132 has a smaller shaft diameter than the shaft diameter of the rotation shaft main body 131. The 1 st bearing portion 132 is rotatably supported by the bearing 11 of the bottom wall 119.

The transmission shaft 133 has a function of transmitting the rotational force of the rotary shaft 3 to the gear pump 111. The shaft diameter of the transmission shaft 133 is smaller than that of the 1 st bearing 132. The transmission shaft 133 protrudes to the gear pump 111 side through the bearing 11. The transmission shaft 133 is disposed in the rotation shaft through hole 121 of the bottom wall 119. A cylindrical adapter 136 is fitted to the outer peripheral surface of the transmission shaft 133. The adapter 136 rotates integrally with the transmission shaft 133. The gear pump 111 side of the adapter 136 protrudes toward the gear pump 111 side with respect to the bottom wall 119. The protruding portion is connected to a gear pump 111.

The 2 nd bearing 134 has a smaller axial diameter than the rotation shaft main body 131. The 2 nd bearing portion 134 is rotatably supported by the bearing 14 of the front flange 10.

The coupling shaft 135 is coupled to a power source such as an engine, not shown. The coupling shaft 135 has a smaller shaft diameter than the 2 nd bearing 134. The tip end of the connecting shaft 135 protrudes outside the front flange 10 via the bearing 14. The oil seal 15 prevents foreign matter from entering between the tip end portion and the front flange 10. A 1 st spline 135a is formed at the tip of the coupling shaft 135. A power source such as an engine, not shown, is coupled to the rotary shaft 3 via the 1 st spline 135 a.

The 2 nd spline 131a is formed in the rotation shaft main body 131. A cylinder 4 is fitted to the rotation shaft main body 131 at a portion corresponding to the 2 nd spline 131 a.

The cylinder 4 is formed in a cylindrical shape. A through hole 16 into which the rotary shaft 3 can be inserted or pressed is formed at the radial center of the cylinder 4. The through hole 16 is also formed with splines 16 a. The spline 16a is spline-coupled to a 2 nd spline 131a of the rotary shaft body 131. Thereby, the rotary shaft 3 rotates integrally with the cylinder 4.

A recess 20 is formed in a section from the axial center of the through hole 16 to the end 4a closer to the bottom wall 119 so as to surround the rotation shaft 3. In a section from the axial center of the through hole 16 to the front flange 10 side, a through hole 25 penetrating the cylinder 4 in the axial direction is formed in a part of the inner peripheral surface. In the recess 20, a spring 23 and retainers 24a, 24b discussed later are housed. A coupling member 26, which will be discussed later, is accommodated in the through hole 25 in an axially movable manner.

Further, a plurality of cylinder holes 17 are formed in the cylinder block 4 so as to surround the periphery of the rotary shaft 3. The cylinder holes 17 are arranged at equal intervals in the circumferential direction. Further, the cylinder hole 17 is formed along the axial direction, and the side of the cylinder hole 17 closer to the front flange 10 is open. Communication holes 18 for communicating the cylinder holes 17 with the outside of the cylinder block 4 are formed in the end portion 4a of the cylinder block 4 at positions corresponding to the cylinder holes 17.

A disc-shaped valve plate 19 is provided at the end 4a of the cylinder block 4 so as to overlap the end face of the end 4 a. The valve plate 19 is fixed to the housing main body 9. Even when the cylinder block 4 rotates together with the rotary shaft 3, the valve plate 19 is stationary with respect to the main casing 2 (casing main body 9).

A supply port 19a and a discharge port, not shown, which communicate with the communication holes 18 of the cylinder block 4 are formed in the valve plate 19 so as to penetrate through the valve plate 19 in the thickness direction. Each cylinder hole 17 communicates with the 1 st communication path 124 formed in the housing main body 9 via the supply port 19a of the valve plate 19 and the communication hole 18 of the cylinder block 4. Further, each cylinder hole 17 communicates with the 3 rd communication path 128 formed in the housing main body 9 through a discharge port, not shown, of the valve plate 19 and the communication hole 18 of the cylinder block 4.

Since the valve plate 19 is fixed to the housing main body 9, the cylinder hole 17 switches between a state in which the hydraulic oil is supplied from the 1 st suction path 122 through the valve plate 19 and a state in which the hydraulic oil is discharged to the 1 st discharge path 123 in accordance with the rotation state of the cylinder block 4.

The piston 21 is housed in each cylinder bore 17 so that the piston 21 can slide in the axial direction. The piston 21 is housed in the cylinder hole 17, and the piston 21 revolves around the center axis C of the rotary shaft 3 as the rotary shaft 3 and the cylinder 4 rotate.

A spherical projection 28 is integrally formed at the end of the piston 21 on the front flange 10 side. In addition, the interior of the piston 21 is formed as a cavity. The cavity is filled with the working oil in the cylinder bore 17. Thus, the reciprocating motion of the piston 21 is associated with the supply and discharge of the working oil with respect to the cylinder bore 17. That is, when the piston 21 is pulled out from the cylinder hole 17, the working oil is supplied from the 1 st suction path 122 into the cylinder hole 17 through the 1 st communication path 124 and the supply port 19 a. When the piston 21 enters the cylinder bore 17, the hydraulic oil is discharged from the cylinder bore 17 through a discharge port not shown and the 1 st discharge path 123.

The spring 23 housed in the recess 20 of the cylinder 4 is, for example, a coil spring. The spring 23 is compressed between two holders 24a, 24b housed in the recess 20. Therefore, the spring 23 generates a biasing force in the extending direction due to its elastic force. The biasing force of the spring 23 is transmitted to the coupling member 26 via one holder 24b of the two holders 24a, 24 b. A pressing member 27 is fitted to the outer peripheral surface of the rotary shaft main body 131 at a position closer to the front flange 10 than the connecting member 26. The biasing force of the spring 23 is transmitted to the pressing member 27 via the coupling member 26.

The front flange 10 has a swash plate 5 provided on an inner surface 10a on the housing main body 9 side. The sloping plate 5 is arranged to be tiltable relative to the front flange 10. The swash plate 5 has a function of restricting displacement of each piston 21 in the axial direction by inclining relative to the front flange 10. A through hole 32 through which the rotation shaft 3 can pass is formed in the radial center of the swash plate 5. A flat sliding surface 5a is formed on the swash plate 5 on the cylinder block 4 side. A plurality of shoes 22 are slidably disposed on the sliding surface 5 a.

The plurality of shoes 22 are attached to the convex portion 28 of the piston 21. A spherical concave portion 22a is formed on the surface of the portion of the shoe 22 that receives the convex portion 28 so as to match the shape of the convex portion 28. The convex portion 28 of the piston 21 is fitted into the concave portion 22 a. Thereby, the shoe 22 is rotatably connected to the convex portion 28 of the piston 21. Each shoe 22 is integrally held by a shoe holding member 29. The pressing member 27 abuts on the shoe holding member 29, and the shoe holding member 29 is pressed toward the swash plate 5 by the pressing member 27. Thereby, the shoe 22 slides so as to follow the sliding surface 5a of the swash plate 5. The inclination angle of the swash plate 5 is controlled by an actuator, not shown.

(Gear pump)

The gear pump 111 includes: a gear case (corresponding to the 2 nd case in the claims) 141 in a rectangular parallelepiped shape, which is disposed on the outer surface 119b of the bottom wall 119 of the main case 2; and two gears 142 and 143 (a drive gear 142 and a driven gear 143) supported rotatably in the gear housing 141 and meshing with each other. A 2 nd suction path (corresponding to a 2 nd suction portion in claims) 144 communicating with the 2 nd communication path 125 of the main casing 2 is formed in a wall surface (corresponding to a 1 st wall surface in claims) 141a of the gear casing 141 overlapping the main casing 2. The 2 nd suction path 144 communicates the inside and outside of the wall surface 141a of the gear housing 141.

In addition, an adapter through-hole 149 is formed in a wall surface 141a of the gear housing 141 at a position corresponding to the rotation shaft through-hole 121 of the main housing 2. The end of the adapter 136 on the gear pump 111 side protrudes into the gear housing 141 through the adapter through hole 149.

The attachment plate 145 is integrally formed on two side wall surfaces 141b and 141c (the 1 st side wall surface 141b and the 2 nd side wall surface 141c) that are orthogonal to the wall surface 141a of the gear housing 141 and that face each other in the radial direction. Of the two side wall surfaces 141b and 141c, the 1 st side wall surface 141b faces the 1 st side surface 119c of the main casing 2 in which the suction port 122a is formed. Of the two side wall surfaces 141b and 141c, the 2 nd side wall surface (corresponding to the 2 nd wall surface in claims) 141c faces the 2 nd side surface 119d of the main casing 2 in which the discharge port 123a is formed.

Each mounting plate 145 extends radially outward. Each mounting plate 145 is used to fix the gear housing 141 to the main casing 2.

A recess 146 is formed in each mounting plate 145 so as to be partially removed from the tip end toward the corresponding sidewall surface 141b, 141 c. A bolt (corresponding to a fixing member in claims) 147 for fixing the gear housing 141 to the main housing 2 penetrates the recess 146.

Here, the concave portion 146 formed in the attachment plate 145 on the 1 st side wall surface 141b side is located on the axis of the female screw portion 127 formed in the 1 st suction path 122 of the main casing 2. That is, the bolt 147 inserted through the recess 146 formed in the attachment plate 145 on the 1 st side wall surface 141b side is fastened to the female screw portion 127.

On the other hand, a bolt 147 inserted through a recess 146 formed in the attachment plate 145 on the 2 nd side wall surface 141c side is fastened to an unillustrated female screw portion formed in the main casing 2. The female screw portion, not shown, and the 1 st discharge path 123 of the main casing 2 are not located at positions that interfere with each other.

Further, a 2 nd discharge path (corresponding to a 2 nd discharge portion in claims) 148 is formed on the 2 nd side wall surface 141c of the gear housing 141. The discharge port 148a of the 2 nd discharge path 148 opens at the 2 nd side wall surface 141 c. In this way, discharge port 148a of gear housing 141 and discharge port 123a of main housing 2 are formed on side wall surface 141c and side surface 119d facing in the same direction.

The two gears 142 and 143 disposed in the gear housing 141 are disposed between the 2 nd suction path 144 and the 2 nd discharge path 148. The arrangement direction of the two gears 142, 143 is orthogonal to the arrangement direction of the 2 nd suction path 144 and the 2 nd discharge path 148.

Of the two gears 142 and 143, the drive gear 142 is coupled to an adapter 136 that protrudes from the main casing 2 through an adapter penetration hole 149. Thereby, the rotational force of the rotary shaft 3 in the main pump 1 is transmitted to the drive gear 142 via the adapter 136. The driven gear 143 of the two gears 142, 143 meshes with the drive gear 142, and therefore rotates in synchronization with the drive gear 142.

(action of Pump Unit)

Next, the operation of the pump unit 110 will be described.

First, the operation of the main pump 1 will be described.

The main pump 1 outputs a driving force based on discharge of the hydraulic oil from the cylinder bore 17 (and supply of the hydraulic oil to the cylinder bore 17).

More specifically, the rotary shaft 3 is rotated by power from a power source such as an engine, and the cylinder block 4 and the rotary shaft 3 rotate integrally. The piston 21 revolves around the center axis C of the rotary shaft 3 with the rotation of the cylinder 4.

Regardless of the inclination angle of the swash plate 5, the shoes 22 attached to the convex portions 28 of the pistons 21 are properly pressed against the sliding surface 5a of the swash plate 5 following the sliding surface 5a of the swash plate 5 by the biasing force of the spring 23. The convex portion 28 of the piston 21 is formed in a spherical shape, and the concave portion 22a of the shoe 22 into which the convex portion 28 is fitted is also formed in a spherical shape. Further, each shoe 22 is pressed toward the swash plate 5 by the pressing member 27 via the shoe holding member 29. Therefore, even if the inclination angle of the swash plate 5 changes, the shoes 22 follow the inclination of the swash plate 5 and properly follow the sliding surface 5a and are pressed against the sliding surface 5 a.

When the piston 21 revolves around the center axis C of the rotary shaft 3 as the cylinder block 4 rotates, the shoes 22 slide on the sliding surface 5a of the swash plate 5 while revolving around the center axis C of the rotary shaft 3. Thereby, each piston 21 slides in the axial direction in each cylinder bore 17, and each piston 21 reciprocates. Thus, the swash plate 5 restricts displacement of each piston 21 in the direction along the axial direction. In response to the reciprocating motion of the piston 21, the hydraulic oil is discharged from a part of the cylinder bores 17 through the 1 st discharge path 123 and the discharge port 13 a. In addition, the working oil is sucked into the other cylinder bores 17 through the suction port 122a and the 1 st suction path 122.

Here, a convex portion 126 protruding into the 1 st suction path 122 is provided on the inner surface 122b of the 1 st suction path 122. The convex portion 126 is disposed at the center in the width direction of the 1 st suction passage 122 that is orthogonal to the direction in which the hydraulic oil flows in the 1 st suction passage 122 (the vertical direction in fig. 2, and the horizontal direction in fig. 3), and therefore, a large difference in flow rate between the hydraulic oil on the right side and the left side with respect to the convex portion 126 in the width direction of the 1 st suction passage 122 can be suppressed.

When the inclination angle of the swash plate 5 (sliding surface 5a) changes, the stroke (sliding distance) of the reciprocating motion of the piston 21 changes. That is, the larger the inclination angle of the swash plate 5, the larger the supply amount and discharge amount of the hydraulic oil to the cylinder bores 17 generated by the reciprocation of each piston 21. On the other hand, the smaller the inclination angle of the swash plate 5, the smaller the supply amount and discharge amount of the hydraulic oil to the cylinder bores 17, which are generated in accordance with the reciprocation of the pistons 21. When the inclination angle of the swash plate 5 is 0 degree, each piston 21 does not reciprocate even if the piston 21 revolves around the center axis C of the rotary shaft 3. Therefore, the discharge amount of the hydraulic oil from each cylinder bore 17 is also zero.

Next, the operation of the gear pump 111 will be described.

The drive gear 142 of the gear pump 111 is coupled to the rotary shaft 3 of the main pump 1 via the adapter 136, and therefore rotates integrally with the rotary shaft 3. Then, the driven gear 143 meshing with the drive gear 142 also rotates in synchronization with the drive gear 142. Then, the working oil flowing through the 1 st suction path 122 is sucked into the 2 nd suction path 144 via the 2 nd communication path 125 of the main casing 2. Then, the hydraulic oil passes between the gears 142 and 143 and the inner surface of the gear case 141, and flows toward the 2 nd discharge path 148. Then, the working oil is discharged through the discharge port 148 a.

In the above embodiment, the convex portion 126 protruding into the 1 st suction passage 122 is provided on the inner surface 122b of the 1 st suction passage 122. The female screw portion 127 formed on the outer surface 119b of the bottom wall 119 enters the convex portion 126. Therefore, even in the case where the female screw portion 127 for fixing the gear housing 141 is to be formed in the bottom wall 119 of the main casing 2 through which the 1 st suction path 122 passes, the female screw portion 127 can be appropriately formed without thickening the bottom wall 119. The pump unit 110 can be reduced in size by suppressing the axial length of the pump unit 110 from becoming longer by the amount corresponding to the necessity of thickening the bottom wall 119.

In addition, the female screw portion 127 is formed in the bottom wall 119 of the main pump 1 on the center axis C of the rotary shaft 3. That is, the gear pump 111 is disposed on the bottom wall 119, and the main pump 1 and the gear pump 111 can be integrated. Therefore, the rotary shaft 3 and the drive gear 142 of the gear pump 111 can be easily coupled to each other via the adapter 136. Therefore, it is not necessary to separately provide a mechanism for driving the gear pump 111, the pump unit 110 can be downsized, and the driving efficiency of the pump unit 110 can be improved.

The convex portion 126 formed in the 1 st suction path 122 is disposed at the center in the width direction of the 1 st suction path 122. Therefore, the flow rate difference of the hydraulic oil on the right side and the left side with respect to the convex portion 126 in the width direction of the 1 st suction path 122 can be suppressed from becoming large. As a result, the disturbance of the flow of the hydraulic oil in the 1 st suction passage 122 can be minimized, and the flow of the hydraulic oil can be stabilized. Thus, the driving efficiency of the pump unit 110 can be further improved.

Further, a discharge port 123a formed in the 1 st discharge path 123 of the main pump 1 is formed in the 2 nd side surface 119d of the bottom wall 119. A discharge port 148a formed in the 2 nd discharge path 148 of the gear pump 111 is formed in the 2 nd side wall surface 141c of the gear housing 141. Since the 2 nd side surface 119d and the 2 nd side wall surface 141c face in the same direction, the discharge port 123a of the 1 st discharge path 123 and the discharge port 148a of the 2 nd discharge path 148 are disposed adjacent to each other. Therefore, the work of connecting the pipes to the discharge paths 123 and 148 (the discharge ports 123a and 148a) and the work of routing the pipes can be easily performed.

In addition, the 1 st suction path 122 of the main pump 1 and the 2 nd suction path 144 of the gear pump 111 communicate via the 2 nd communication path 125. Therefore, by supplying the hydraulic oil only to the 1 st suction path 122, the hydraulic oil can be guided to both the main pump 1 and the gear pump 111. Therefore, the structures of the suction paths 122 and 144 can be simplified, and the pump unit 110 can be further downsized.

The present invention is not limited to the above-described embodiments, and various modifications may be made to the above-described embodiments without departing from the scope of the present invention.

For example, in the above-described embodiment, the hydraulic pump unit 110 used in the construction machine 100 such as the excavator is described. However, the above-described structure of the convex portion 126 can be applied to various pump units for sucking and discharging liquid, without being limited thereto.

In the above-described embodiment, the case where the convex portion 126 has a substantially cylindrical shape has been described. However, the present invention is not limited thereto, and various shapes can be adopted. For example, the convex portion 126 may be formed as described in the following modification.

(modification example)

Fig. 4 is a cross-sectional view along the axial direction showing a modification of the convex portion 126. Fig. 4 corresponds to the drawing of the periphery of the 1 st suction path 122 in fig. 2. Fig. 5 is a sectional view taken along line B-B of fig. 4.

As shown in fig. 4 and 5, the convex portion 126 may have an elliptic conical shape. Specifically, the bottom side of the convex portion 126 is formed in an elliptical shape, and the convex portion 126 becomes tapered as it goes toward the protruding direction. The major axis J of the projection 126 is along the direction in which the hydraulic oil flows in the 1 st suction path 122 (the vertical direction in fig. 4 and 5).

Therefore, the same effects as those of the above-described embodiment can be obtained by adopting the above-described modification. Further, since the projection 126 is formed in an elliptic conical shape and the major axis J thereof is along the direction in which the hydraulic oil flows in the 1 st suction path 122, the flow path resistance to the hydraulic oil by the projection 126 can be minimized, and the disturbance of the flow of the hydraulic oil in the 1 st suction path 122 can be reliably suppressed. Thus, the driving efficiency of the pump unit 110 can be reliably improved.

In the above-described embodiment, the case where the convex portion 126 is formed in the 1 st suction path 122 of the main casing 2 and the female screw portion 127 is formed in the convex portion 126 is described. However, the present invention is not limited to this, and the convex portion 126 may be formed in the 1 st discharge path 123 and the female screw portion 127 may be formed in the convex portion 126 (see the convex portion 126 indicated by the two-dot chain line in fig. 2) depending on the shape of the gear pump 111. Further, the convex portion 126 may be formed in both the 1 st suction path 122 and the 1 st discharge path 123.

In the above-described embodiment, the case where the gear housing 141 is fastened and fixed to the main housing 2 by the female screw portion 127 and the bolt 147 is described. However, various methods can be employed for fixing the gear case 141 to the main case 2. For example, rivets or the like may be used instead of the bolts 147. In this case, a hole into which a rivet can be pressed may be formed in the main casing 2 instead of the female screw portion 127. That is, a hole for fixing the gear case 141 to the convex portion 126 may be formed from the outer surface 119b side of the gear case 141 to be fixed.