JPH05256269A - Fluid machine - Google Patents

Abstract

PURPOSE:To form in light weight and in small size a fluid operating system and a fluid machine such as a pump used in this system. CONSTITUTION:A set of vane-type fluid machine (example, oil hydraulic pump) 1, used in common for a fluid operating system in a plurality of systems such as automobile power steering and cooling fan drive systems, has operating chambers 111 and 112 independent of each other. For instance, a delivery pressure of the operating chamber 111 is introduced to a hydraulic reaction force chamber 147 through a delivery port 131, back pressure grooves 331, 335, flow path 431, back pressure groove 531, fit-insertion hole 831 for a vane, back pressure groove 532, flow path 433, circumferential groove 536, and a flow path 435. In the other hand, the pressure is introduced to a hydraulic reaction force chamber 145 through a flow path 432 from the back pressure groove 335, to act so as to cancel radial directional force by the delivery pressure of the operating chamber 111, and a share load of bearings 151, 152 is decreased.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a vane type fluid machine such as a hydraulic pump or a compressor having a plurality of working chambers arranged in parallel inside one unit.

[0002]

2. Description of the Related Art As a pump for driving two fluid actuation systems such as a power steering system for automobiles and a cooling fan drive system, for example, two hydraulic pumps are used separately, or two pumps are coaxially used. There is a tandem type in which the hydraulic pumps on the stand are arranged. However, when two hydraulic pumps are used, a large mounting space is required, and even in the case of the tandem type, there is a limit to downsizing due to its physical size and weight. On the other hand, in the case of the parallel type, since one pump has two working chambers, it can be made smaller and lighter than the tandem type.

Generally, inside the pump, the respective working chambers are arranged so that a pressure imbalance does not occur between the respective working chambers. However, when the arrangement of the respective working chambers is not axisymmetric, the pressures are An unbalanced state causes an unbalanced axial load due to the pressure difference between the working chambers, so it is necessary to strengthen the bearings and increase the shaft diameter in order to improve strength and durability. It becomes a factor to prevent the change. In the case of the tandem type, the two working chambers are eccentrically arranged in two directions and arranged axially symmetrically, and the discharge ports of both working chambers and the suction ports are formed to communicate with each other in the housing. Basically, pressure imbalance does not occur between the working chambers, but in the case of parallel type, if two fluid working systems of one pump are independently configured,
Even if two working chambers are eccentrically arranged in two directions and arranged axially symmetrically, since the respective discharge ports and the suction ports of both working chambers are not in communication with each other, the working pressures of the two fluid working systems are At different times, a pressure imbalance occurs between the working chambers, and a very large unbalanced axial load is generated depending on the pressure difference between the working chambers.

[0004]

SUMMARY OF THE INVENTION The present invention is a means for reducing or eliminating pressure imbalance between working chambers in a parallel type vane pump having the above-mentioned problems, generally speaking, a parallel type fluid machine. It is an object of the present invention to provide a fluid machine that is equipped with, and is small and lightweight, and that can simultaneously drive two systems (a plurality of systems) of fluid actuation system.

[0005]

As a means for solving the above problems, the present invention rotatably rotatably supports a rotor in a housing and forms a working chamber between the rotor and a cam ring. In a vane type fluid machine in which a plurality of vanes are slidably inserted in the radial direction, the working chambers are eccentrically formed in a plurality of directions and are formed at a plurality of places, and the respective working chambers are independent of each other. A control mechanism for controlling the fluid actuation system is disposed between the fluid actuation system and at least one actuation chamber separately connected to the fluid actuation system of the system, and the pressure is increased in each actuation chamber. The working fluid is configured to independently drive a plurality of fluid working systems corresponding to the working chambers, and the working chambers are provided on the outer peripheral surface supporting the rotor. Axisymmetrically side in correspondence with forming each independently a reaction chamber, communicates with the back pressure groove and the passage in each independently of the reaction chamber corresponding thereto and each working chamber,
By introducing the discharge pressure of each working chamber into each reaction force chamber, the force generated in each working chamber can be canceled by the force generated in each reaction chamber. I will provide a.

[0006]

When the fluid machine is driven to rotate, the plurality of vanes slide in the radial direction due to the centrifugal force as the rotor rotates, bringing the tips into contact with the inner peripheral surface of the cam ring, and thus the sealed working chamber. Formed at multiple locations. The respective working chambers pump the working fluid under pressure to the respective control mechanisms of the plurality of fluid working systems which are independent of each other, and at the same time, the discharge pressure of each working chamber is independent of the back pressure groove and the back pressure groove. Since it is introduced into the reaction force chamber formed on the outer peripheral surface of the rotor, for example, the support portion of the rotor, on the side of axial symmetry with respect to each working chamber via the flow path, the radial force generated in each working chamber is , The radial force to be supported by the rotor bearing is the difference between these forces, offset by the forces generated in each reaction chamber in the opposite direction, and if the forces are perfectly balanced, the bearing Since the load on the bearing is zero, it is possible to make the bearing smaller than that without the reaction force chamber, and it is not necessary to use a strong bearing. Moreover, 1
Since individual working chambers are formed at multiple locations around each rotor, one fluid machine can be shared by multiple independent fluid working systems. It is possible to reduce the weight.

[0007]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS The construction of the working chamber and hydraulic reaction chamber of a parallel hydraulic pump is shown in FIGS. 2 to 7, and the construction of two fluid working systems using a parallel hydraulic pump is shown in FIG. As shown in FIGS. 2 to 4, the pump 1 includes a rotor 11, a plurality of vanes 12, a cam ring 13, a side plate (front side plate 141, rear side plate 142) shaft 15, and a housing 16 (front housing 16).
1, the rear housing 162). Rotor 1
1 is a cam ring 13 fixedly housed in a housing 16.
In addition to being rotatably supported inside, the working chambers 111 and 112 (see FIG. 1) are provided between the rotor 11 and the inner peripheral surface of the cam ring 13.
Is also formed eccentrically in two directions.

A shaft 15 has bearings 151, 152 between the front housing 161 and the rear housing 162.
It is rotatably installed by. Shaft 15 is rotor 1
1 is connected by spline fitting or key fitting. A plurality of vanes 12 are fitted in the rotor 11 so as to be slidable in the radial direction (see FIG. 1). The rear side plate 1 is provided between the cam ring 13 and the rear housing 162.
42 and the front housing 161
Front side plates 141 are respectively provided between and (see FIGS. 2 to 4). The front side plate 141 is pressed toward the cam ring 13 by the biasing member 17, and the front side plate 141, the cam ring 13, the rear side plate 142, and the rear housing 162 are in close contact with each other. Rear side plate 1
42 is a working chamber 111 corresponding to the fluid working system 2.
Suction port 132 and discharge port 131 are formed, and the working chamber 1 corresponding to the fluid working system 3 is formed.
A suction port 134 and a discharge port 133 for 12 are each formed (see also FIG. 1).

The suction port 132 is connected to the oil storage device 4 such as a reserve tank through a suction port 632 formed in the rear housing 162 in communication with the suction port 132, and a flow passage 732 and a flow passage 730 (FIG. 1, FIG. 1). 2). Similarly, the suction port 134 is formed in the rear housing 162 so as to communicate with the suction port 634, the flow passage 734, and the flow passage 730.
It is connected to the oil storage device 4 via. Discharge port 131
Is connected to the actuating device 22 through a control mechanism 21 such as a control valve formed in the rear housing 162, through a discharge port 631 and a flow path 731 formed in the rear housing 162 in communication with it (FIG. 1 and FIG.
reference). Similarly, the discharge port 133 is connected to the actuating device 32 via the control mechanism 31 via the discharge port 633 formed in the rear housing 162 and the flow path 733 in communication therewith (see also FIG. 4).

Further, as shown in FIGS. 3, 5, and 6,
Corresponding to the working chamber 111, the rear side plate 142 has a back pressure groove 331 between it and the front side surface of the rear housing 162, an arc-shaped back pressure groove 335, and an arc-shaped back pressure groove between it and the rear side surface of the rotor 11. Channels 431 are formed to communicate with each other between the groove 531 and the back pressure grooves 335 and 531. Similarly, as shown in FIGS. 4, 5, and 6, the back pressure groove 333, the arc-shaped back pressure groove 337, and the rotor 11 corresponding to the working chamber 112 are formed between the rear housing 162 and the front side surface. Arc-shaped back pressure groove 533 between the rear side surface and the back pressure groove 3
Channels 433 are formed between 33 and 533 so as to communicate with each other.

Further, as shown in FIG. 1, the rotor 11 is formed with the same number of fitting holes as the plurality of vanes 12, and these holes are fitted to the working chamber 111 as the vanes 12 rotate.
Two types of fitting holes 83, which are fitting holes corresponding to the working chamber 112.
1, 833 (see FIGS. 2 to 4), the working chamber 11
Corresponding to No. 1, the fitting insertion hole 831 is always the back pressure groove 5 regardless of rotation.
31 and the fitting insertion hole 833 corresponding to the working chamber 112 is always in communication with the back pressure groove 533 regardless of rotation (see also FIG. 6).

Further, two arcuate grooves are formed on the rear side inner peripheral surface of the rear side plate 142 so as to face each other independently, and the rotor 1 is fitted into the rear side plate 142.
The hydraulic reaction force chambers 145 and 146 are formed between the outer peripheral surface of 1 and the outer peripheral surface of 1 (see FIGS. 3, 4, and 5). And reaction chamber 14
5 and the back pressure groove 335 between the flow path 432 and the reaction force chamber 14
6 and the back pressure groove 337, the flow paths 434 are formed so as to communicate with each other. Thereby, the discharge pressure of the working chamber 111 is introduced into the reaction force chamber 145 through the discharge port 131, the back pressure grooves 331 and 335, and the flow path 432, and the discharge pressure of the working chamber 112 is changed to the discharge port 133 and the back pressure groove. 333, 337,
It is introduced into the reaction force chamber 146 via the flow path 434.

Also, as shown in FIG. 7, arc-shaped back pressure grooves 532 and 534 are respectively formed between the front side plate 141 and the front side surface of the rotor 11, and a front housing is provided on the front side. Circumferential grooves 535 and 536 are formed between the rear side surface of 161 and the rear side surface. Then, as shown in FIG. 3, a flow path 433 is provided between the back pressure groove 532 and the circumferential groove 536, and as shown in FIG.
Flow paths 437 are formed to communicate with each other between the groove 34 and the circumferential groove 535.

Further, two arcuate grooves are independently formed on the inner peripheral surface of the front side plate 141 so as to face each other.
Between the outer peripheral surface of the rotor 11 and the hydraulic reaction force chambers 147, 148
Are formed respectively (see FIGS. 3 and 4). And reaction chamber 1
Between the groove 47 and the circumferential groove 536, a flow path 435 (see FIG. 3),
Flow paths 436 are formed to communicate between the reaction force chamber 148 and the circumferential groove 535 (see FIG. 4).

As a result, as shown in FIG. 3, the working chamber 1
The discharge pressure of 11 is the discharge port 131, the back pressure grooves 331, 3
35, the flow path 431, the back pressure groove 531, the fitting insertion hole 831, the back pressure groove 532, the flow path 433, the circumferential groove 536, and the flow path 435.
4 and is introduced into the reaction force chamber 147 through the discharge port 13 as shown in FIG.
3, back pressure groove 333, 337, flow path 433, back pressure groove 53
3, the insertion hole 833, the back pressure groove 534, the flow path 437, the circumferential groove 535, and the flow path 436 are introduced into the reaction force chamber 148.

As the control mechanisms 21 and 31, any means having a flow rate adjusting action such as a flow control valve can be used, and the flow rate to the operating devices 22 and 32 can be increased by increasing the pump rotation speed. The surplus working fluid is recirculated to the suction ports 132 and 134 via the flow paths 732 and 734, respectively. In addition, the flow path 73
2, 734 are both partially or wholly formed in communication with a flow path 730 formed in communication with the oil storage device 4, and are used for both suction of working fluid and recirculation of excess working fluid. Combined use.

As is clear from the above description, the structural features of the illustrated embodiment according to the present invention are configured such that one vane type hydraulic pump is opposed to each other so that pumps for two systems can be independently operated. Then, the discharge pressure of each working chamber is introduced into a hydraulic reaction force chamber formed at a position axisymmetrical to each working chamber through some back pressure groove, flow passage, fitting hole, and circumferential groove. That is the configuration. In the present invention, the fluid actuation system is not limited to two systems, and even in the case of a plurality of fluid actuation systems, the same parallel configuration can be adopted.

When the pump 1 is operated, the plurality of vanes 12 slide in the radial direction due to the centrifugal force as the rotor 11 rotates, and rotate while the tips of the vanes 12 are in contact with the inner peripheral surface of the cam ring 13. In the fluid actuation system 2, as shown in FIGS. 1 and 2, the working fluid is stored in the oil storage device 4,
After being sucked through the flow paths 730 and 732 and the suction ports 632 and 132, the pressure in the working chamber 111 is increased, the pressure is discharged from the discharge port 131, and the discharge port 631 and the flow path 731 are discharged as shown in FIG. It is sent to the control mechanism 21 via the.

During pressurization in the working chamber 111, the fitting port 831 of the vane 12 has a discharge port 131 and a back pressure groove 3.
The discharge pressure of the working chamber 111 is introduced through 31, 335, the flow path 431, and the back pressure groove 531. This makes vane 1
The bottom portion of 2 has a high pressure, and the tip portion is pressed against the inner peripheral surface of the cam ring 13 and does not separate, so that the sealability is maintained and the pressure is increased. In addition, the excess working fluid due to the increase in the pump rotation speed or the like is controlled by the flow rate adjusting action of the control mechanism 21, so that the reflux flow passage 732 and the suction ports 632 and 132 are provided.
It is returned to the working chamber 111 via (see FIGS. 1 to 3).

In the fluid actuating system 3, as shown in FIGS. 1 to 4, the working fluid passes through the oil storage device 4, the flow passages 730 and 734, and the suction ports 634 and 134 in the same manner as the fluid actuating system 2. After being sucked and boosted in the working chamber 112, it is discharged from the discharge port 133 and sent to the control mechanism 31 via the discharge port 633 and the flow path 733. The discharge port 1 is inserted into the fitting hole 833 of the vane 12.
The discharge pressure of the working chamber 112 is introduced through the 33, the back pressure grooves 333, 337, the flow path 433, and the back pressure groove 533.
The excess working fluid in the control mechanism 31 is returned to the working chamber 112 again via the recirculation flow path 734 and the suction ports 634 and 134. The parallel vane pump is
The pump basically operates as described above.

In the pump 1 of the illustrated embodiment, the pressure imbalance is reduced or eliminated in the following manner. When the pump 1 operates and the pressure in the working chambers 111 and 112 rises, the discharge pressure in the working chamber 111 passes through the discharge port 131, the back pressure grooves 331 and 335, and the one through the flow path 432, the rear housing of the rotor 11 While being introduced into the reaction force chamber 145 on the 162 side, the other side includes the flow path 431, the back pressure groove 531,
Fitting hole 831, back pressure groove 532, flow path 433, circumferential groove 53
6, and is introduced into the reaction force chamber 147 on the front housing 161 side of the rotor 11 via the flow path 435 (see FIG. 3 and the like). Further, the discharge pressure of the working chamber 112 is the discharge port 13
3, through the back pressure grooves 333, 337, and one through the flow path 434, the reaction force chamber 1 on the rear housing 162 side of the rotor 11
46, and the other is the flow path 433, the back pressure groove 5
33, the insertion hole 833, the back pressure groove 534, the flow path 437, the circumferential groove 535, and the flow path 436, and is introduced into the reaction force chamber 148 on the front housing 161 side of the rotor 11 (see FIG. 4 and the like). ..

That is, the discharge pressures of the working chambers 111 and 112 go through the above-mentioned paths, and the hydraulic reaction force chambers 145, 1 which are arranged on the axially symmetrical side of the working chambers 111 and 112.
47 and 146, 148 respectively. Thus, for example, focusing on the fluid actuation system 2 (FIG. 1),
The rotor 11 is drawn according to the pressure in the working chamber 111 (Fig. 3).
A downward force is generated in the reaction force chambers 145,
Due to the pressure introduced into 147, an upward force is generated in the drawing (FIG. 3) and acts on the rotor 11. On this occasion,
If the pressure receiving areas in the reaction force chambers 145 and 147 are equal to or substantially equal to the pressure receiving area in the working chamber 111, the vertical forces acting on the rotor 11 are canceled and eliminated.
Alternatively, it can be greatly reduced. Even in the case of the fluid actuation system 3, the upward force and the reaction force chambers 146 and 148 in the drawing (FIG. 4) due to the pressure in the actuation chamber 112.
The downward forces in the drawing due to the internal pressure (FIG. 4) are canceled out as in the case of the fluid actuation system 2. as a result,
Since the bearings 151 and 152 are lightly loaded, it is not necessary to use a strong bearing, and the bearing, and thus the entire size can be reduced in size and weight. Note that the fluid operation system is not limited to two systems, and even in the case of a fluid operation system in which three or more systems are merged in parallel, the same action and effect can be obtained by using the same configuration.

[0023]

According to the present invention, a fluid machine such as a single vane pump can be used as a parallel type machine by forming a plurality of working chambers around a rotor and sharing it with a plurality of fluid working systems. At the same time, the discharge pressure is introduced into the reaction force chamber to cancel the radial force due to the discharge pressure of the working chamber, so the burden on the bearing is significantly lightened and it is not necessary to use a powerful large bearing. As a result, the fluid machine and the fluid actuation system as a whole can be reduced in weight and size.

[Brief description of drawings]

FIG. 1 is a configuration diagram of a fluid working system including a working chamber sectional view of a parallel vane pump as an embodiment of the present invention.

FIG. 2 is a cross-sectional view taken along the line AA showing the structure on the suction side of the parallel vane pump of the embodiment.

FIG. 3 is a BB cross-sectional view showing the structures of the discharge side and the hydraulic reaction chamber of one fluid actuating system in the same pump.

FIG. 4 is a C-C cross-sectional view showing the structures of the discharge side and the hydraulic reaction chamber of the other fluid actuation system in the same pump.

FIG. 5 is an EE cross-sectional view showing a back pressure groove and a flow path formed in the rear side plate of the same pump.

FIG. 6 is an F-F cross-sectional view showing a back pressure groove and a flow path formed in the rear side plate.

FIG. 7 is a GG sectional view showing a back pressure groove and a flow path formed in the front side plate 141.

[Explanation of symbols]

DESCRIPTION OF SYMBOLS 1 ... Pump 2, 3 ... Fluid actuation system 4 ... Oil storage device 11 ... Rotor 12 ... Vane 13 ... Cam ring 15 ... Shaft 16 ... Housing 21, 22 ... Control mechanism 111, 112 ... Working chamber 131, 133 ... Discharge port 132, 134 ... suction port 141 ... front side plate 142 ... rear side plate 145, 146, 147, 148 ... reaction force chamber 151, 152 ... bearing 161 ... front housing 162 ... rear housing 331, 333, 335, 337 ... back pressure groove 431, 432 , 433, 434, 435, 436, 4
37 ... Flow path 531,532,533,534 ... Back pressure groove 535,536 ... Circumferential groove 631,633 ... Discharge port 632,634 ... Suction port 730,731,732,733,734 ... Flow path 831,833 ... Insertion hole

 ─────────────────────────────────────────────────── ─── Continuation of the front page (72) Inventor Mitsuo Inagaki 14 Iwatani, Shimohakaku-cho, Nishio-shi, Aichi Japan Auto Parts Research Institute, Inc. (72) Inventor Hideaki Sasaya 1-1, Showa-cho, Kariya, Aichi Within Nippondenso Co., Ltd.

Claims (1)

[Claims] 1. A vane type fluid machine in which a rotor is rotatably supported in a housing, a working chamber is formed between the rotor and a cam ring, and a plurality of vanes are slidably inserted in the rotor in a radial direction. In the above, the working chambers are formed in a plurality of locations by being eccentric in a plurality of directions, and each working chamber is separately connected to a plurality of independent fluid working systems, and at least one working chamber is provided. A control mechanism for controlling the fluid actuation system is disposed between the chamber and the fluid actuation system, and a plurality of systems of fluid actuation systems corresponding to the actuation chambers are provided by the working fluid pressurized in each actuation chamber. The reaction chambers are configured to be driven independently of each other, and reaction chambers are independently formed on the axisymmetric side on the outer peripheral surface supporting the rotor in correspondence with each working chamber. The moving chamber and the reaction chamber corresponding to it communicate with each other independently by the back pressure groove and the flow path, and the discharge pressure of each working chamber is introduced into each reaction chamber, so that the force generated in each working chamber. Is constructed so that it can be canceled by a force generated in each reaction force chamber.