CN216478120U - Hydraulic pump source system - Google Patents

Abstract

The utility model provides a hydraulic pump source system, which comprises a main working cylinder, an oil tank and a pressurizing oil supply device, wherein the pressurizing oil supply device comprises a first supercharger, a second supercharger, a working pump and an oil supplementing pump, the working pump is suitable for connecting the oil tank with the low-pressure cavities of the first supercharger and the second supercharger and injecting oil in the oil tank into the low-pressure cavity of the first supercharger or the low-pressure cavity of the second supercharger; the oil supplementing pump is suitable for connecting the oil tank with the high-pressure cavities of the first supercharger and the second supercharger and injecting oil in the oil tank into the high-pressure cavity of the first supercharger or the high-pressure cavity of the second supercharger; and the high-pressure cavities of the first supercharger and the second supercharger are both connected with the working cavity of the main working cylinder and are suitable for alternately supplying oil to the working cavity of the main working cylinder. The utility model discloses a set up working pump and oil supplementing pump in order to be the low-pressure chamber and the high-pressure chamber fuel feeding of booster respectively, reduced the manufacturing degree of difficulty, cost, installed power and the energy consumption of working pump and oil supplementing pump, and reduced the control degree of difficulty of hydraulic pump source system.

Description

Hydraulic pump source system

Technical Field

The utility model relates to a hydraulic system technical field particularly, relates to a hydraulic pump source system.

Background

At present, in hydraulic systems, such as large tonnage hydraulic presses, pump devices that supply the low pressure chambers of the intensifier structures are also commonly used to supply the high pressure chambers of the intensifier structures. This requires the pump device to satisfy a certain power, not only increases the manufacturing difficulty and manufacturing cost of the pump device, but also increases the installed power, energy consumption and control difficulty of the hydraulic system.

SUMMERY OF THE UTILITY MODEL

The utility model provides a problem be: how to reduce the manufacturing difficulty and cost of the pump device and simultaneously reduce the control difficulty of the hydraulic system.

In order to solve the above problems, the present invention provides a hydraulic pump source system, which includes a main working cylinder, an oil tank and a pressurizing oil supply device, wherein the pressurizing oil supply device includes a first supercharger, a second supercharger, a working pump and an oil supply pump, the working pump is suitable for connecting the oil tank with the low pressure cavities of the first supercharger and the second supercharger, and injecting the oil in the oil tank into the low pressure cavity of the first supercharger or the low pressure cavity of the second supercharger; the oil supplementing pump is suitable for connecting the oil tank with the high-pressure cavities of the first supercharger and the second supercharger and injecting oil in the oil tank into the high-pressure cavity of the first supercharger or the high-pressure cavity of the second supercharger; and the high-pressure cavities of the first supercharger and the second supercharger are connected with the working cavity of the main working cylinder and are suitable for alternately supplying oil to the working cavity of the main working cylinder.

Optionally, the oil replenishment pump is a low pressure high flow pump.

Optionally, the pressure boosting oil supply device further comprises a pipeline structure and a valve assembly, the pipeline structure comprises a fifth pipeline and a sixth pipeline, the fifth pipeline is suitable for connecting the high-pressure cavity of the first pressure booster and the working cavity of the main working cylinder, and the sixth pipeline is suitable for connecting the high-pressure cavity of the second pressure booster and the working cavity of the main working cylinder; the valve assembly comprises a first supercharger high-pressure cavity oil discharge one-way valve and a second supercharger high-pressure cavity oil discharge one-way valve, and the first supercharger high-pressure cavity oil discharge one-way valve and the second supercharger high-pressure cavity oil discharge one-way valve are suitable for being arranged on the fifth pipeline and the sixth pipeline respectively.

Optionally, the pipeline structure further includes a third pipeline and a fourth pipeline, the third pipeline is suitable for connecting the high-pressure cavity of the first supercharger with the oil-replenishing pump, and the fourth pipeline is suitable for connecting the high-pressure cavity of the second supercharger with the oil-replenishing pump; the valve assembly further comprises a first supercharger high-pressure cavity oil supplementing one-way valve and a second supercharger high-pressure cavity oil supplementing one-way valve, and the first supercharger high-pressure cavity oil supplementing one-way valve and the second supercharger high-pressure cavity oil supplementing one-way valve are respectively suitable for being arranged on the third pipeline and the fourth pipeline.

Optionally, the pipeline structure further comprises a first pipeline adapted to connect the working pump with the low pressure chamber of the first supercharger and a second pipeline adapted to connect the working pump with the low pressure chamber of the second supercharger; the valve assembly further comprises a first supercharger valve group and a second supercharger valve group, wherein the first supercharger valve group comprises a first supercharger low-pressure side oil inlet proportional valve suitable for being arranged on a first pipeline, and the second supercharger valve group comprises a second supercharger low-pressure side oil inlet proportional valve suitable for being arranged on a second pipeline.

Optionally, the pipeline structure still includes seventh pipeline and eighth pipeline, first booster valves still includes first booster low pressure side oil return proportional valve, second booster valves still includes second booster low pressure side oil return proportional valve, the low pressure chamber of first booster passes through first booster low pressure side oil return proportional valve with seventh tube coupling the oil tank, the low pressure chamber of second booster passes through second booster low pressure side oil return proportional valve with eighth tube coupling the oil tank.

Optionally, the supercharging oil supply device further comprises an energy accumulator, one end of the first pipeline is connected with the low-pressure cavity of the first supercharger through the first supercharger low-pressure side oil inlet proportional valve, one end of the second pipeline is connected with the low-pressure cavity of the second supercharger through the second supercharger low-pressure side oil inlet proportional valve, and the other end of the first pipeline is communicated with the other end of the second pipeline and is connected with the working pump through the energy accumulator; the accumulator is adapted to accumulate the oil supplied from the working pump and supply the oil to the low pressure chamber of the first supercharger or the second supercharger.

Optionally, the accumulator includes high-pressure gas liquid jar and high-pressure gas tank group, high-pressure gas tank group is suitable for doing high-pressure gas liquid jar is aerifyd, high-pressure gas liquid jar is suitable for storing the oil that the working pump provided and for first booster or the low pressure chamber fuel feeding of second booster.

Optionally, the pipeline structure further includes a ninth pipeline adapted to connect an oil outlet of the oil replenishment pump with the oil tank, and the valve assembly further includes a regulating valve adapted to be disposed on the ninth pipeline.

Optionally, the valve assembly further includes a master cylinder oil drain valve, the pipeline structure further includes a tenth pipeline adapted to connect the working chamber of the master cylinder with the oil tank, and the master cylinder oil drain valve is adapted to be disposed on the tenth pipeline.

Compared with the prior art, the utility model, following beneficial effect has: the working pump and the oil supplementing pump are arranged to respectively supply oil to the low-pressure cavity and the high-pressure cavity of the supercharger, on one hand, the oil supplementing pressure of the high-pressure cavity required by the return stroke of the piston of the supercharger is very low, so that the oil supplementing pump can meet the requirements by adopting pumps with low manufacturing cost, low manufacturing difficulty and low power consumption, such as a low-pressure large-flow pump and the like, and correspondingly, the working pump only needs to inject oil into the low-pressure cavity of the supercharger, so that the structure of the working pump can be simplified, and meanwhile, the manufacturing cost, the manufacturing difficulty and the power consumption of the working pump and the oil supplementing pump required by the prior art are reduced, namely, the arrangement of the working pump and the oil supplementing pump reduces the manufacturing difficulty and the manufacturing cost of the working pump and the installed power and the energy consumption of a hydraulic pump source system; on the other hand, the structure is simple compared with the arrangement of the working pump and the oil supplementing pump in the prior art, the control difficulty of the working pump and the oil supplementing pump is reduced, and the control difficulty of the hydraulic pump source system is reduced. Two groups of superchargers (a first supercharger and a second supercharger) are arranged to supply oil for the working cavity wheel flow of the main working cylinder, so that the continuity and stability of the oil supply of the working cavity of the main working cylinder are ensured, and the main working cylinder can be continuously and stably operated.

Drawings

Fig. 1 is a schematic structural diagram of a hydraulic pump source system in an embodiment of the present invention.

Description of reference numerals:

1-a main working cylinder; 2-an oil tank; 3-a first supercharger; 4-a second supercharger; 5-a working pump; 6-oil supplement pump; 7-pipeline structure, 71-first pipeline, 72-second pipeline, 73-third pipeline, 74-fourth pipeline, 75-fifth pipeline, 76-sixth pipeline, 77-seventh pipeline, 78-eighth pipeline, 79-ninth pipeline, 70-tenth pipeline; 8-a valve assembly, 81-a first supercharger valve group, 811-a first supercharger low-pressure side oil inlet proportional valve, 812-a first supercharger low-pressure side oil return proportional valve, 82-a second supercharger valve group, 821-a second supercharger low-pressure side oil inlet proportional valve, 822-a second supercharger low-pressure side oil return proportional valve, 83-a first supercharger high-pressure cavity oil supplementing one-way valve, 84-a second supercharger high-pressure cavity oil supplementing one-way valve, 85-a first supercharger high-pressure cavity oil discharge one-way valve, 86-a second supercharger high-pressure cavity oil discharge one-way valve, 88-a main working cylinder oil discharge valve and 89-an adjusting valve; 9-energy accumulator, 91-high pressure gas liquid tank, 92-high pressure gas tank group.

Detailed Description

In order to make the aforementioned objects, features and advantages of the present invention more comprehensible, embodiments accompanied with figures are described in detail below.

It should be noted that the terms "first," "second," and the like in the description and claims of the present invention and in the drawings described above are used for distinguishing between similar elements and not necessarily for describing a particular sequential or chronological order. It is to be understood that the data so used is interchangeable under appropriate circumstances such that the embodiments of the invention described herein are capable of operation in sequences other than those illustrated or otherwise described herein.

With reference to fig. 1, an embodiment of the present invention provides a hydraulic pump source system, including a main working cylinder 1, an oil tank 2 and a pressurizing oil supply device, where the pressurizing oil supply device includes a first supercharger 3, a second supercharger 4, a working pump 5 and an oil replenishing pump 6, the working pump 5 is adapted to connect the oil tank 2 with low-pressure cavities of the first supercharger 3 and the second supercharger 4, and injects oil in the oil tank 2 into the low-pressure cavity of the first supercharger 3 or the low-pressure cavity of the second supercharger 4; the oil replenishing pump 6 is suitable for connecting the oil tank 2 with the high-pressure cavities of the first supercharger 3 and the second supercharger 4 and injecting oil in the oil tank 2 into the high-pressure cavity of the first supercharger 3 or the high-pressure cavity of the second supercharger 4; and the high pressure chambers of the first supercharger 3 and the second supercharger 4 are both connected with the working chamber of the main working cylinder 1 and are suitable for alternately supplying oil to the working chamber of the main working cylinder 1.

In this embodiment, the hydraulic pump source system is suitable for hydraulic equipment such as an oil press and an extruder. The pressurizing oil supply device of the hydraulic pump source system is used for continuously supplying high-pressure oil to the main working cylinder 1 so as to ensure the stable operation of the main working cylinder 1. Specifically, the superchargers (i.e., the first supercharger 3 and the second supercharger 4) of the superchargers oil supply apparatus are hydraulic cylinder structures such as piston cylinders having a cylinder body and a piston disposed in the cylinder body and adapted to move in the cylinder body, and a high-pressure chamber and a low-pressure chamber of the superchargers are disposed at both ends of the piston, respectively. The superchargers of the supercharging oil supply device are provided with two groups, namely a first supercharger 3 and a second supercharger 4, a working pump 5 of the supercharging oil supply device is suitable for connecting an oil tank 2 with a low-pressure cavity of the first supercharger 3 and a low-pressure cavity of the second supercharger 4, wherein an oil inlet of the working pump 5 is connected with the oil tank 2, and an oil outlet of the working pump 5 is respectively connected with the low-pressure cavity of the first supercharger 3 and the low-pressure cavity of the second supercharger 4 through different pipelines (described in detail later) so as to inject oil (hydraulic oil) in the oil tank 2 into the low-pressure cavity of the first supercharger 3 or the low-pressure cavity of the second supercharger 4 (namely, the oil injection of the low-pressure cavity of the first supercharger 3 and the oil injection of the low-pressure cavity of the second supercharger 4 are not performed simultaneously but performed alternately to ensure the normal operation of the superchargers). Similarly, the oil supply pump 6 of the supercharging oil supply device is adapted to connect the oil tank 2 with the high-pressure chamber of the first supercharger 3 and the high-pressure chamber of the second supercharger 4, wherein an oil inlet of the oil supply pump 6 is connected with the oil tank 2, and an oil outlet of the oil supply pump 6 is respectively connected with the high-pressure chamber of the first supercharger 3 and the high-pressure chamber of the second supercharger 4 through different pipelines, so as to inject the oil (hydraulic oil) in the oil tank 2 into the high-pressure chamber of the first supercharger 3 or the high-pressure chamber of the second supercharger 4 (i.e. the oil injection into the high-pressure chamber of the first supercharger 3 and the high-pressure chamber of the second supercharger 4 is not performed simultaneously, but performed alternately, so as to ensure the normal operation of the superchargers). When the working pump 5 is used for filling oil into the low-pressure cavity of the first supercharger 3 (the second supercharger 4) (the piston of the supercharger moves towards the high-pressure cavity and discharges and supplies hydraulic oil in the high-pressure cavity to the working cavity of the main working cylinder 1), the oil supplementing pump 6 is used for filling oil into the high-pressure cavity of the second supercharger 4 (the first supercharger 3) (the piston of the supercharger moves towards the low-pressure cavity and discharges the hydraulic oil in the low-pressure cavity back to the oil tank 2) so as to realize that the first supercharger 3 and the second supercharger 4 alternately supply oil to the working cavity of the main working cylinder 1, realize continuous oil supply and stable oil supply of the main working cylinder 1, avoid the situation that the large change of flow and pressure causes strong impact and vibration on parts such as the main working cylinder 1 to cause damage of a hydraulic pump source system, and ensure the stable operation of the main working cylinder 1.

At present, in hydraulic systems, such as large tonnage hydraulic presses, pump devices that supply the low pressure chambers of the intensifier structures are also commonly used to supply the high pressure chambers of the intensifier structures. This requires the pump device to satisfy a certain power, not only increases the manufacturing difficulty and manufacturing cost of the pump device, but also increases the installed power, energy consumption and control difficulty of the hydraulic system. In this embodiment, the working pump 5 and the oil replenishment pump 6 are arranged to supply oil to the low-pressure cavity and the high-pressure cavity of the supercharger respectively, on one hand, the oil replenishment pump 6 can meet the requirements by adopting pumps with low manufacturing cost, low manufacturing difficulty and low power consumption, such as a low-pressure large-flow pump, and the like, as the high-pressure cavity oil replenishment pressure required by the piston return stroke of the supercharger is very low, and correspondingly, the working pump 5 only needs to inject oil to the low-pressure cavity of the supercharger, so that the structure of the working pump 5 can be simplified, and meanwhile, the manufacturing cost, the manufacturing difficulty and the power consumption required by the working pump 5 in comparison with the prior art are reduced, that is, the arrangement of the working pump 5 and the oil replenishment pump 6 reduces the manufacturing difficulty, the manufacturing cost and the installed power and the energy consumption of the hydraulic pump source system of the working pump 5 and the oil replenishment pump 6; on the other hand, the arrangement of the working pump 5 and the oil supplementing pump 6 which have simpler structures than the prior art reduces the control difficulty of the working pump 5 and the oil supplementing pump 6 and reduces the control difficulty of a hydraulic pump source system. The working cavity of the main working cylinder 1 is subjected to wheel flow oil supply by arranging two groups of superchargers (a first supercharger 3 and a second supercharger 4), so that the continuity and stability of oil supply of the working cavity of the main working cylinder 1 are ensured, and the main working cylinder 1 can be continuously and stably operated.

Optionally, the oil replenishment pump 6 is a low pressure high flow pump.

In this embodiment, the oil replenishing pump 6 is preferably a low-pressure large-flow pump, so as to reduce the manufacturing cost, the manufacturing difficulty and the installation power of the oil replenishing pump 6 while ensuring that the oil replenishing pump 6 can provide sufficient pressure for the high-pressure cavity of the supercharger.

Optionally, as shown in fig. 1, the supercharging oil supply device further includes a pipeline structure 7 and a valve assembly 8, the pipeline structure 7 includes a fifth pipeline 75 and a sixth pipeline 76, the fifth pipeline 75 is adapted to connect the high-pressure cavity of the first supercharger 3 with the working cavity of the main working cylinder 1, and the sixth pipeline 76 is adapted to connect the high-pressure cavity of the second supercharger 4 with the working cavity of the main working cylinder 1; valve assembly 8 includes a first booster high pressure chamber drain check valve 85 and a second booster high pressure chamber drain check valve 86, first booster high pressure chamber drain check valve 85 and second booster high pressure chamber drain check valve 86 being adapted to be disposed on fifth pipeline 75 and sixth pipeline 76, respectively.

In this embodiment, the components of the hydraulic pump source system are communicated with each other through the pipeline structure 7, so as to be used for the circulation of hydraulic oil. The valve assembly 8 is arranged on the pipeline structure 7 and used for controlling the on-off of the corresponding pipeline structure 7 so as to control the circulation of hydraulic oil in the corresponding pipeline structure 7. The working chamber of the main working cylinder 1 is connected with the high-pressure chamber of the first supercharger 3 and the high-pressure chamber of the second supercharger 4 through a fifth pipeline 75 and a sixth pipeline 76, so that the high-pressure chamber of the first supercharger 3 and the high-pressure chamber of the second supercharger 4 alternately supply oil to the working chamber of the main working cylinder 1, and thus continuous oil supply and stable oil supply of the main working cylinder 1 are realized. Furthermore, a first supercharger high-pressure chamber oil drain check valve 85 and a second supercharger high-pressure chamber oil drain check valve 86 are respectively arranged on the fifth pipeline 75 and the sixth pipeline 76, wherein an oil inlet of the first supercharger high-pressure chamber oil drain check valve 85 (the second supercharger high-pressure chamber oil drain check valve 86) is connected with the high-pressure chamber of the first supercharger 3 (the second supercharger 4) through the fifth pipeline 75 (the sixth pipeline 76), an oil outlet of the first supercharger high-pressure chamber oil drain check valve 85 (the second supercharger high-pressure chamber oil drain check valve 86) is connected with the working chamber of the main working cylinder 1 through the fifth pipeline 75 (the sixth pipeline 76), so that the hydraulic oil flowing through the fifth pipeline 75 (the sixth pipeline 76) is suitable for directionally flowing towards the working chamber of the main working cylinder 1, and the pressure of the working chamber of the main working cylinder 1 is the same as the pressure of the high-pressure chamber of the supercharger.

Optionally, as shown in fig. 1, the pipeline structure 7 further includes a third pipeline 73 and a fourth pipeline 74, the third pipeline 73 is adapted to connect the high-pressure cavity of the first supercharger 3 with the oil-replenishing pump 6, and the fourth pipeline 74 is adapted to connect the high-pressure cavity of the second supercharger 4 with the oil-replenishing pump 6; the valve assembly 8 further includes a first booster high-pressure cavity oil-supplementing check valve 83 and a second booster high-pressure cavity oil-supplementing check valve 84, the first booster high-pressure cavity oil-supplementing check valve 83 and the second booster high-pressure cavity oil-supplementing check valve 84 being adapted to be disposed on the third pipeline 73 and the fourth pipeline 74, respectively.

In this embodiment, an oil inlet of the oil supply pump 6 is connected to the oil tank 2, and an oil outlet of the oil supply pump 6 is connected to the high-pressure chamber of the first supercharger 3 and the high-pressure chamber of the second supercharger 4 through a third pipeline 73 and a fourth pipeline 74, respectively, so as to inject oil (hydraulic oil) in the oil tank 2 into the high-pressure chamber of the first supercharger 3 or the high-pressure chamber of the second supercharger 4. The first supercharger high-pressure cavity oil-supplementing one-way valve 83 and the second supercharger high-pressure cavity oil-supplementing one-way valve 84 are respectively arranged on the third pipeline 73 and the fourth pipeline 74, an oil outlet of the first supercharger high-pressure cavity oil-supplementing one-way valve 83 (the second supercharger high-pressure cavity oil-supplementing one-way valve 84) is connected with a high-pressure cavity of the first supercharger 3 (the second supercharger 4) through the third pipeline 73 (the fourth pipeline 74), an oil inlet of the first supercharger high-pressure cavity oil-supplementing one-way valve 83 (the second supercharger high-pressure cavity oil-supplementing one-way valve 84) is connected with an oil outlet of the oil-supplementing pump 6 through the third pipeline 73 (the fourth pipeline 74), and therefore hydraulic oil flowing through the third pipeline 73 (the fourth pipeline 74) is suitable for directionally flowing towards the high-pressure cavity of the first supercharger 3 (the second supercharger 4).

Optionally, as shown in fig. 1, the pipe structure 7 further includes a first pipe 71 adapted to connect the working pump 5 with the low-pressure chamber of the first supercharger 3, and a second pipe 72 adapted to connect the working pump 5 with the low-pressure chamber of the second supercharger 4; valve assembly 8 further includes a first booster valve block 81 and a second booster valve block 82, first booster valve block 81 including a first booster low pressure side oil intake proportional valve 811 adapted to be disposed on first conduit 71, and second booster valve block 82 including a second booster low pressure side oil intake proportional valve 821 adapted to be disposed on second conduit 72.

In this embodiment, an oil inlet of the working pump 5 is connected to the oil tank 2, and an oil outlet of the working pump 5 is connected to the low pressure chamber of the first supercharger 3 and the low pressure chamber of the second supercharger 4 through the first pipeline 71 and the second pipeline 72, respectively, so as to inject the hydraulic oil in the oil tank 2 into the low pressure chamber of the first supercharger 3 or the low pressure chamber of the second supercharger 4. A first supercharger low-pressure side oil inlet proportional valve 811 and a second supercharger low-pressure side oil inlet proportional valve 821 are respectively arranged on the first pipeline 71 and the second pipeline 72 and are respectively suitable for controlling the on-off of the first pipeline 71 and the on-off of the second pipeline 72. The working pump 5 alternately supplies oil to the low-pressure cavity of the first supercharger 3 and the low-pressure cavity of the second supercharger 4 by alternately opening and closing the first supercharger low-pressure side oil inlet proportional valve 811 and the second supercharger low-pressure side oil inlet proportional valve 821.

For the hydraulic pump source system, for convenience of description, a group of pressure boosters (e.g., the first pressure booster 3) is described below as an example; in an initial state, oil discharged by the oil replenishing pump 6 enters a high-pressure cavity of the first supercharger 3 through the third pipeline 73, and then hydraulic oil injected into the high-pressure cavity of the first supercharger 3 enters a working cavity of the main working cylinder 1 through the fifth pipeline 75 until the pressure in the working cavity of the main working cylinder 1 is the same as the pressure in the high-pressure cavity of the first supercharger 3, and then the first supercharger high-pressure cavity oil discharge one-way valve 85 is closed; thereafter (during the pressurization process of the hydraulic pump source system), as the oil supply pump 6 continues to supply oil through the third line 73, the piston of the first pressure booster 3 moves toward the low-pressure chamber and discharges the hydraulic oil in the low-pressure chamber (by opening the first pressure booster low-pressure side oil return proportional valve 812, which will be described later). Until the piston of the first supercharger 3 moves to the lower limit towards the low-pressure cavity, the first supercharger low-pressure side oil inlet proportional valve 811 is opened, the main working pump 5 and the accumulator 9 (described later) drive the hydraulic oil in the oil tank 2 to enter the low-pressure cavity of the first supercharger 3 through the first pipeline 71 and the first supercharger low-pressure side oil inlet proportional valve 811, the piston of the first supercharger 3 moves towards the high-pressure cavity and discharges the hydraulic oil in the high-pressure cavity, namely the hydraulic oil in the high-pressure cavity of the first supercharger 3 enters the working cavity of the main working cylinder 1 through the first supercharger high-pressure cavity oil discharge one-way valve 85 and the fifth pipeline 75 under the drive of the piston thereof, so as to provide high-pressure oil for the working cavity of the main working cylinder 1; until the piston of the supercharger moves to the upper limit towards the high-pressure cavity, the oil discharge one-way valve 85 of the high-pressure cavity of the first supercharger and the oil inlet proportional valve 811 of the low-pressure side of the first supercharger are closed (meanwhile, the oil return proportional valve 812 of the low-pressure side of the first supercharger is opened), the oil supplementing pump 6 continues to supply oil to the high-pressure cavity of the first supercharger 3 through the third pipeline 73 and drives the piston of the first supercharger to move towards the low-pressure cavity, and therefore reciprocating automatic circulation is achieved, and reciprocating movement of the piston of the supercharger is achieved. In this way, the movement direction of the piston of the first supercharger 3 is controlled by the alternate opening and closing of the first supercharger low-pressure side oil inlet proportional valve 811 and the first supercharger low-pressure side oil return proportional valve 812, and the action is stable; similarly, the direction of movement of the piston of the second supercharger 4 is also controlled by the alternating opening and closing of the second supercharger low-pressure side oil-in proportional valve 821 and the second supercharger low-pressure side oil-return proportional valve 822. Thus, because the two groups of superchargers (namely the first supercharger 3 and the second supercharger 4) are arranged, in the supercharging process of the hydraulic pump source system, when the piston of one group of superchargers moves towards the high-pressure cavity and outputs high-pressure oil to the main working cylinder 1, the high-pressure cavity of the other group of superchargers drives the piston of the other group of superchargers to move towards the low-pressure cavity through oil supplement of the oil supplement pump 6, and the two groups of superchargers supply oil to the main working pump 5 alternately, so that continuous oil supply of the main working pump 5 is realized.

The reciprocating motion of the piston of the first supercharger 3 is controlled by the alternate opening and closing of the first supercharger low-pressure side oil-in proportional valve 811 and the first supercharger low-pressure side oil-return proportional valve 812; the reciprocating motion of the piston of the second supercharger 4 is controlled by the alternate opening and closing of the second supercharger low-pressure side oil-in proportional valve 821 and the second supercharger low-pressure side oil-out proportional valve 822. When the piston of the first supercharger 3 moves towards the high-pressure cavity and outputs high-pressure oil to the main working cylinder 1 (the low-pressure side oil inlet proportional valve 811 of the first supercharger is opened, and the low-pressure side oil return proportional valve 812 of the first supercharger is closed), the high-pressure cavity of the second supercharger 4 drives the piston to move towards the low-pressure cavity thereof by oil supplement of the oil supplement pump 6 and discharges oil to the oil return tank 2 (the low-pressure side oil inlet proportional valve 821 of the second supercharger is closed, and the low-pressure side oil return proportional valve 822 of the second supercharger is opened); when the high-pressure chamber of the first supercharger 3 drives the piston to move towards the low-pressure chamber thereof by oil supplement of the oil supplement pump 6 and oil is discharged and returned to the oil tank 2 (the first supercharger low-pressure side oil inlet proportional valve 811 is closed, and the first supercharger low-pressure side oil return proportional valve 812 is opened), the piston of the second supercharger 4 moves towards the high-pressure chamber thereof and outputs high-pressure oil to the main working cylinder 1 (the second supercharger low-pressure side oil inlet proportional valve 821 is opened, and the second supercharger low-pressure side oil return proportional valve 822 is closed). In this way, the two groups of superchargers are used as the main working pump 5 to alternately supply oil, and continuous oil supply of the main working pump 5 is realized. Moreover, through the matching between the first supercharger low-pressure side oil inlet proportional valve 811, the first supercharger low-pressure side oil return proportional valve 812, the second supercharger low-pressure side oil inlet proportional valve 821 and the second supercharger low-pressure side oil return proportional valve 822, the control stability and the adjustability of the first supercharger 3 and the second supercharger 4 are realized, the stability of the total output flow of the first supercharger 3 and the second supercharger 4 is ensured, namely, the continuity and the stability of the oil supply of the main working pump 5 are ensured, the control difficulty of a hydraulic pump source system is reduced, and the control precision of the hydraulic pump source system is improved.

In addition, when the starting point and the end point of the two groups of superchargers coincide, in order to ensure the flow balance and seamless butt joint of output flow, the piston of one group of superchargers needs to be decelerated when reaching the end point (reaching the upper limit or the lower limit), and the piston of the other group of superchargers needs to be accelerated when just beginning to extend (leaving the upper limit or the lower limit); when the pistons of the first group of superchargers decelerate to zero and begin to move in the other direction, the piston speed of the second group of superchargers is maximized, thus ensuring no change in output flow and thus ensuring continuous and smooth oil supply of the main working pump 5.

Optionally, as shown in fig. 1, the pipeline structure 7 further includes a seventh pipeline 77 and an eighth pipeline 78, the first pressure booster valve group 81 further includes a first pressure booster low-pressure side oil return proportional valve 812, the second pressure booster valve group 82 further includes a second pressure booster low-pressure side oil return proportional valve 822, the low-pressure cavity of the first pressure booster 3 is connected to the oil tank 2 through the first pressure booster low-pressure side oil return proportional valve 812 and the seventh pipeline 77, and the low-pressure cavity of the second pressure booster 4 is connected to the oil tank 2 through the second pressure booster low-pressure side oil return proportional valve 822 and the eighth pipeline 78.

In this embodiment, the first supercharger low-pressure side oil return proportional valve 812 and the second supercharger low-pressure side oil return proportional valve 822 are respectively arranged on the seventh pipeline 77 and the eighth pipeline 78, and are respectively used for controlling the on-off of the seventh pipeline 77 and the eighth pipeline 78, and are also respectively used for discharging oil from the low-pressure cavity of the first supercharger 3 to the oil tank 2 and discharging oil from the low-pressure cavity of the second supercharger 4 to the oil tank 2. In the supercharging process of the hydraulic pump source system, when the piston of one group of superchargers (for example, the first supercharger 3) moves towards the low-pressure cavity (also when the first supercharger low-pressure side oil inlet proportional valve 811 is closed), the first supercharger low-pressure side oil return proportional valve 812 corresponding to the first supercharger 3 is simultaneously opened, so that the low-pressure cavity of the first supercharger 3 is discharged to the oil tank 2 through the first supercharger low-pressure side oil return proportional valve 812 and the seventh pipeline 77, and smooth movement of the piston of the first supercharger 3 is ensured. When the piston of the first supercharger 3 moves to the lower limit towards the low-pressure chamber, the first supercharger low-pressure side oil inlet proportional valve 811 is opened, and the first supercharger low-pressure side oil return proportional valve 812 is closed, so as to close (disconnect) the seventh pipeline 77, and avoid the seventh pipeline 77 from being opened to influence the injection of the hydraulic oil into the low-pressure chamber of the supercharger. Similarly, the second supercharger low-pressure side oil return proportional valve 822 is also used for draining the low-pressure cavity of the second supercharger 4 to the oil tank 2, and the switching of the first supercharger low-pressure side oil return proportional valve 812 and the second supercharger low-pressure side oil return proportional valve 822 is suitable for being performed alternately, so that the low-pressure cavity of the first supercharger 3 and the low-pressure cavity of the second supercharger 4 are drained alternately, and therefore, the continuous oil supply of the main working cylinder 1 is ensured through the two superchargers.

Optionally, as shown in fig. 1, the supercharged oil supply device further includes an accumulator 9, one end of the first pipeline 71 is connected to the low-pressure cavity of the first supercharger 3 through a first supercharger low-pressure side oil inlet proportional valve 811, one end of the second pipeline 72 is connected to the low-pressure cavity of the second supercharger 4 through a second supercharger low-pressure side oil inlet proportional valve 821, and the other end of the first pipeline 71 is communicated with the other end of the second pipeline 72 and is connected to the working pump 5 through the accumulator 9; the accumulator 9 is adapted to accumulate the oil supplied from the working pump 5 and supply the oil to the low-pressure chamber of the first supercharger 3 or the second supercharger 4.

In this embodiment, the oil outlet of the working pump 5 is connected to the first pipeline 71 and the second pipeline 72 through the accumulator 9, and the accumulator 9 is used for accumulating the oil supplied by the working pump 5, maintaining the oil pressure, and supplying the oil to the low-pressure chamber of the first supercharger 3 or the second supercharger 4. Through setting up energy storage ware 9, can also make the specification of working pump 5 can further reduce, the flow of working pump 5 satisfy the average flow of press action can, like this, greatly reduced required quantity of working pump 5, reduced required specification of working pump 5, reduced manufacturing cost, the degree of difficulty and the installed power of working pump 5 promptly, and reduced the area of working pump 5 and hydraulic pump source system. Furthermore, the accumulator 9 is adapted to eliminate the pulses to reduce or stop the vibrations caused by the large changes in the flow in the first and second lines 71, 72, stabilizing the pressure variations.

Alternatively, as shown in fig. 1, the accumulator 9 includes a high-pressure gas tank 91 and a high-pressure gas tank 92, the high-pressure gas tank 92 is adapted to charge the high-pressure gas tank 91, and the high-pressure gas tank 91 is adapted to accumulate oil supplied from the working pump 5 and supply oil to the low-pressure chamber of the first supercharger 3 or the second supercharger 4.

In a hydraulic system in the prior art, common accumulators 9 for hydraulic oil are all of a bladder type or a piston type and the like, the specifications of the accumulators cannot be too large, and the maximum volume is generally hundreds of liters; for large oil presses, the volume of the accumulator 9 would be very large, and if a conventional accumulator 9 were used, a very large number would be possible (even hundreds of conventional accumulators 9). Therefore, the accumulator 9 in this embodiment adopts a combination of the high-pressure gas-liquid tank 91 and the high-pressure gas tank, and a single pressure container in this form can be dozens of cubes, so that for an ultra-large hydraulic system, several pressure containers are enough, and the cost and the floor area of the accumulator 9 are reduced. Specifically, the high-pressure gas tank group 92 of the accumulator 9 is configured to supply gas such as nitrogen to the high-pressure gas-liquid tank 91, and the high-pressure gas-liquid tank 91 is configured to store oil supplied from the working pump 5, maintain oil pressure (when the working pump 5 fills the high-pressure gas-liquid tank 91 with hydraulic oil, the pressure of the hydraulic oil is equal to the nitrogen pressure, and as the hydraulic oil continues to be filled, the nitrogen pressure increases, and the pressure of the hydraulic oil increases until the hydraulic oil is filled to a set pressure value), and supply oil to the low-pressure chamber of the first supercharger 3 or the second supercharger 4.

Optionally, as shown in fig. 1, the pipeline structure 7 further includes a ninth pipeline 79 adapted to connect an oil outlet of the oil replenishing pump 6 with the oil tank 2, and the valve assembly 8 further includes a regulating valve 89, where the regulating valve 89 is adapted to be disposed on the ninth pipeline 79.

In this embodiment, the ninth pipeline 79 is used for connecting an oil outlet of the oil replenishing pump 6 with the oil tank 2, and the regulating valve 89 is adapted to be arranged on the ninth pipeline 79 and controls on/off of the ninth pipeline 79. The ninth pipeline 79 and the regulating valve 89 are arranged to discharge the redundant hydraulic oil provided by the oil replenishing pump 6 back to the oil tank 2 when needed; for example, in the pressurization process of the hydraulic pump source system, when the flow rate provided by the oil replenishing pump 6 to the high-pressure cavity of the supercharger is greater than the flow rate required by the high-pressure cavity of the supercharger, the regulating valve 89 and the ninth pipeline 79 are opened to discharge the redundant flow rate back to the oil tank 2, so that the oil replenishing pump 6 and the hydraulic pump source system can be operated normally and stably, and a safety protection effect is achieved.

Optionally, the valve assembly 8 further comprises a master cylinder drain valve 88, the line arrangement 7 further comprises a tenth line 70 adapted to connect the working chamber of the master cylinder 1 with the oil tank 2, the master cylinder drain valve 88 being adapted to be arranged on the tenth line 70.

In this embodiment, the master cylinder drain valve 88 is disposed on the tenth pipe 70 for connecting the working chamber of the master cylinder 1 and the oil tank 2, and is configured to control on/off of the tenth pipe 70. When the main working cylinder 1 works, the main working cylinder oil drain valve 88 is closed to ensure the stability of the working cavity pressure of the main working cylinder 1; after the master cylinder 1 completes the operation, the master cylinder drain valve 88 is opened, and the plunger (or piston) of the master cylinder 1 moves toward the working chamber to drain the hydraulic oil in the working chamber into the oil tank 2 through the tenth line 70. In this way, smooth operation of the main cylinder 1 is ensured.

Although the present disclosure has been described above, the scope of the present disclosure is not limited thereto. Various changes and modifications may be made by those skilled in the art without departing from the spirit and scope of the present disclosure, and these changes and modifications are intended to fall within the scope of the present disclosure.

Claims (10)

1. A hydraulic pump source system is characterized by comprising a main working cylinder (1), an oil tank (2) and a boosting oil supply device, wherein the boosting oil supply device comprises a first supercharger (3), a second supercharger (4), a working pump (5) and an oil supplementing pump (6), the working pump (5) is suitable for connecting the oil tank (2) with low-pressure cavities of the first supercharger (3) and the second supercharger (4) and injecting oil in the oil tank (2) into the low-pressure cavity of the first supercharger (3) or the low-pressure cavity of the second supercharger (4); the oil supplementing pump (6) is suitable for connecting the oil tank (2) with the high-pressure cavities of the first supercharger (3) and the second supercharger (4) and injecting oil in the oil tank (2) into the high-pressure cavity of the first supercharger (3) or the high-pressure cavity of the second supercharger (4); and the high-pressure cavities of the first supercharger (3) and the second supercharger (4) are connected with the working cavity of the main working cylinder (1) and are suitable for alternately supplying oil to the working cavity of the main working cylinder (1).

2. Hydraulic pump system according to claim 1, characterized in that the oil supply pump (6) is a low-pressure high-flow pump.

3. The hydraulic pumping system as defined in claim 1 or 2, characterized in that the pressurizing oil supply device further comprises a piping structure (7) and a valve assembly (8), the piping structure (7) comprising a fifth piping (75) and a sixth piping (76), the fifth piping (75) being adapted to connect the high-pressure chamber of the first supercharger (3) with the working chamber of the main working cylinder (1), the sixth piping (76) being adapted to connect the high-pressure chamber of the second supercharger (4) with the working chamber of the main working cylinder (1); the valve assembly (8) comprises a first supercharger high-pressure cavity oil discharge one-way valve (85) and a second supercharger high-pressure cavity oil discharge one-way valve (86), and the first supercharger high-pressure cavity oil discharge one-way valve (85) and the second supercharger high-pressure cavity oil discharge one-way valve (86) are suitable for being arranged on the fifth pipeline (75) and the sixth pipeline (76) respectively.

4. A hydraulic pumping system according to claim 3, characterized in that the line arrangement (7) further comprises a third line (73) and a fourth line (74), the third line (73) being adapted to connect the high-pressure chamber of the first pressure booster (3) with the oil replenishment pump (6), the fourth line (74) being adapted to connect the high-pressure chamber of the second pressure booster (4) with the oil replenishment pump (6); the valve assembly (8) further comprises a first supercharger high-pressure cavity oil supplementing one-way valve (83) and a second supercharger high-pressure cavity oil supplementing one-way valve (84), wherein the first supercharger high-pressure cavity oil supplementing one-way valve (83) and the second supercharger high-pressure cavity oil supplementing one-way valve (84) are respectively suitable for being arranged on the third pipeline (73) and the fourth pipeline (74).

5. The hydraulic pump source system according to claim 4, characterized in that the piping structure (7) further includes a first piping (71) adapted to connect the working pump (5) with the low-pressure chamber of the first supercharger (3) and a second piping (72) adapted to connect the working pump (5) with the low-pressure chamber of the second supercharger (4); valve assembly (8) still include first booster valves (81) and second booster valves (82), first booster valves (81) are suitable for setting up including being in first booster low pressure side oil feed proportional valve (811) on first pipeline (71), second booster valves (82) are suitable for setting up including second booster low pressure side oil feed proportional valve (821) on second pipeline (72).

6. The hydraulic pumping system of claim 5, wherein the piping structure (7) further comprises a seventh piping (77) and an eighth piping (78), the first booster valve group (81) further comprises a first booster low-pressure side oil return proportional valve (812), the second booster valve group (82) further comprises a second booster low-pressure side oil return proportional valve (822), the low-pressure chamber of the first booster (3) is connected to the oil tank (2) through the first booster low-pressure side oil return proportional valve (812) and the seventh piping (77), and the low-pressure chamber of the second booster (4) is connected to the oil tank (2) through the second booster low-pressure side oil return proportional valve (822) and the eighth piping (78).

7. The hydraulic pump source system according to claim 5, wherein the pressure-increasing oil supply device further comprises an accumulator (9), one end of the first pipeline (71) is connected to the low-pressure chamber of the first pressure increasing device (3) through the first pressure increasing device low-pressure side oil inlet proportional valve (811), one end of the second pipeline (72) is connected to the low-pressure chamber of the second pressure increasing device (4) through the second pressure increasing device low-pressure side oil inlet proportional valve (821), and the other end of the first pipeline (71) is communicated with the other end of the second pipeline (72) and is connected to the working pump (5) through the accumulator (9); the accumulator (9) is adapted to accumulate oil provided by the working pump (5) and to supply oil to a low-pressure chamber of the first supercharger (3) or the second supercharger (4).

8. The hydraulic pump source system according to claim 7, characterized in that the accumulator (9) comprises a high pressure gas tank (91) and a high pressure gas tank bank (92), the high pressure gas tank bank (92) being adapted to charge the high pressure gas tank (91), the high pressure gas tank (91) being adapted to store oil provided by the working pump (5) and to supply oil to a low pressure chamber of the first booster (3) or the second booster (4).

9. Hydraulic pump source system according to claim 3, characterized in that said line arrangement (7) further comprises a ninth line (79) adapted to connect an outlet of said oil replenishment pump (6) with said oil tank (2), said valve assembly (8) further comprising a regulating valve (89), said regulating valve (89) being adapted to be arranged on said ninth line (79).

10. A hydraulic pump system according to claim 3, characterized in that the valve assembly (8) further comprises a master cylinder drain valve (88), the line arrangement (7) further comprising a tenth line (70) adapted to connect the working chamber of the master cylinder (1) with the oil tank (2), the master cylinder drain valve (88) being adapted to be arranged on the tenth line (70).

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