CN219119549U - Hydraulic pressurizing system, hydraulic control system and garbage compression box - Google Patents

Abstract

The utility model provides a hydraulic pressurizing system, a hydraulic control system and a garbage compression box, wherein the hydraulic pressurizing system comprises: the oil inlet pipeline and the oil return pipeline are suitable for being connected with the execution oil cylinder; the pressurizing pipeline is connected with the oil inlet pipeline in parallel; the booster valve comprises a valve body and a piston arranged in the valve body, wherein the piston comprises a first piston and a second piston, and the diameter of the first piston is smaller than that of the second piston; the first unidirectional circulation mechanism and the second unidirectional circulation mechanism are respectively arranged at the upstream position and the downstream position of the first oil port; and the switching mechanism is connected with the pressure increasing valve. In the structure, the system oil pressure in the oil inlet pipeline does not need to be continuously increased, continuous pressurization is realized through the pressurization valve on the pressurization pipeline, the system oil pressure is at a lower level, and the overflow heating value is small.

Description

Hydraulic pressurizing system, hydraulic control system and garbage compression box

Technical Field

The utility model relates to the technical field of environmental sanitation equipment, in particular to a hydraulic pressurizing system, a hydraulic control system and a garbage compression box.

Background

The garbage compression box is a common environmental sanitation device, and the pushing head is pushed to extend out through the oil cylinder, so that garbage compression is realized. In the garbage compression process, as the pushing head continuously advances, the pressure born by the oil cylinder is larger and larger, so that the system oil pressure of the hydraulic system is required to be continuously increased, the hydraulic system is in a higher pressure state, the energy consumption is high, and the overflow heating of the hydraulic system is serious.

Disclosure of Invention

Therefore, the utility model aims to overcome the defects of the prior art that the garbage compression box has high system pressure and serious overflow heating when compressing garbage, thereby providing a hydraulic pressurizing system, a hydraulic control system and the garbage compression box.

In order to solve the above problems, the present utility model provides a hydraulic pressurizing system including: the oil inlet pipeline and the oil return pipeline are suitable for being connected with the execution oil cylinder; the pressurizing pipeline is connected with the oil inlet pipeline in parallel; the pressure boosting valve comprises a valve body and a piston arranged in the valve body, the piston comprises a first piston and a second piston, the diameter of the first piston is smaller than that of the second piston, the piston divides the valve body into a high-pressure cavity positioned outside the first piston and a low-pressure cavity positioned outside the second piston, a first oil port communicated with the high-pressure cavity and a second oil port communicated with the low-pressure cavity are arranged on the valve body, and the first oil port is connected with a pressure boosting pipeline; the first unidirectional circulation mechanism and the second unidirectional circulation mechanism are respectively arranged at the upstream position and the downstream position of the first oil port, and are both suitable for unidirectional circulation of hydraulic oil along the direction facing the execution oil cylinder; and the switching mechanism is connected with the pressure increasing valve and is suitable for enabling the second oil port to be communicated with the pressure increasing pipeline or enabling the second oil port to be communicated with the oil return pipeline.

Optionally, the switching mechanism is a first reversing valve, the reversing valve has a first position and a second position, the first reversing valve enables the second oil port to be communicated with the pressurizing pipeline when being in the first position, and the first reversing valve enables the second oil port to be communicated with the oil return pipeline when being in the second position.

Optionally, a rod cavity is formed in a space between the first piston and the second piston, the rod cavity is communicated with the oil return pipeline through a pressure relief pipeline, a third oil port, a fourth oil port and a fifth oil port are arranged on the first reversing valve, the third oil port is communicated with the rod cavity, the fourth oil port is communicated with the second oil port, the fifth oil port is communicated with the pressurizing pipeline, when the reversing valve is in a first position, the third oil port is blocked, and the fourth oil port is communicated with the fifth oil port, when the first reversing valve is in a second position, the fifth oil port is blocked, and the third oil port is communicated with the fourth oil port.

Optionally, the valve body is provided with the sixth hydraulic fluid port, and first piston is at reciprocating motion's in-process, and the sixth hydraulic fluid port can be with high-pressure chamber or have the pole chamber intercommunication, or the sixth hydraulic fluid port is sealed by first piston, and the one end of first switching-over valve is provided with first control pipeline and control spring, and first control pipeline and sixth hydraulic fluid port intercommunication, the other end of first switching-over valve is provided with the second control pipeline, second control pipeline and pressure boost pipeline intercommunication.

Optionally, hydraulic locks are arranged on the oil inlet pipeline and the oil return pipeline.

The utility model also provides a hydraulic control system, comprising: a first hydraulic pump; the first hydraulic pump is communicated with the first oil supply oil way; the oil discharge oil way is suitable for being communicated with an external oil tank; the hydraulic pressurizing system is characterized in that an oil inlet pipeline is communicated with a first oil supply pipeline or an oil discharge pipeline through a second reversing valve, and an oil return pipeline is communicated with the first oil supply pipeline or the oil discharge pipeline through a third reversing valve; the oil inlet pipeline and the oil return pipeline of the first execution oil cylinder are respectively communicated with the rodless cavity and the rod cavity of the first execution oil cylinder.

Optionally, the hydraulic control system further includes a first pressure relief overflow mechanism, the first pressure relief overflow mechanism includes a fourth reversing valve and a first overflow valve, which are disposed in parallel, the fourth reversing valve is adapted to connect or disconnect the first oil supply path and the oil discharge path, and an inlet and an outlet of the first overflow valve are respectively connected with the first oil supply path and the oil discharge path.

Optionally, the hydraulic control system further comprises: a second oil supply passage; the second hydraulic pump is communicated with the first oil supply oil way or the second oil supply oil way through a fifth reversing valve; the second execution oil cylinder is communicated with the second oil supply oil way and the oil discharge oil way through a sixth reversing valve.

Optionally, the hydraulic control system further includes a second pressure relief overflow mechanism, the second pressure relief overflow mechanism includes a seventh reversing valve and a second overflow valve that are disposed in parallel, the seventh reversing valve is adapted to connect or disconnect the second oil supply path and the oil discharge path, and an inlet and an outlet of the second overflow valve are respectively connected with the second oil supply path and the oil discharge path.

The utility model also provides a garbage compression box, which comprises the hydraulic control system.

The utility model has the following advantages:

by utilizing the technical scheme of the utility model, hydraulic oil is supplied to the execution cylinder from the oil inlet pipeline. Meanwhile, a booster valve is arranged on the booster pipeline, when the switching mechanism enables the second oil port to be communicated with the oil return pipeline, the low-pressure cavity is depressurized, and hydraulic oil enters the high-pressure cavity from the booster pipeline through the first oil port. When the switching structure enables the second oil port to be communicated with the pressurizing pipeline, the low-pressure cavity is filled with oil, and the high-pressure cavity is compressed. Since the diameter of the first piston is smaller than that of the second piston, pressurized hydraulic oil is output from the first oil port to the pressurizing pipe and supplied to the execution cylinder. The switching mechanism drives the piston to reciprocate through the reciprocating communication of the second oil port, the pressurizing pipeline and the oil return pipeline, so that continuous pressurizing is realized. In the structure, the system oil pressure in the oil inlet pipeline does not need to be continuously increased, continuous pressurization is realized through the pressurization valve on the pressurization pipeline, the system oil pressure is at a lower level, and the overflow heating value is small. Therefore, the technical scheme of the utility model solves the defects of high system pressure and serious overflow heating of the garbage compression box in the prior art when compressing garbage.

Drawings

In order to more clearly illustrate the embodiments of the present utility model or the technical solutions in the prior art, the drawings that are needed in the description of the embodiments or the prior art will be briefly described, and it is obvious that the drawings in the description below are some embodiments of the present utility model, and other drawings can be obtained according to the drawings without inventive effort for a person skilled in the art.

FIG. 1 shows a schematic structural diagram of an embodiment of a hydraulic control system of the present utility model;

FIG. 2 shows a schematic diagram of the hydraulic boosting system of the hydraulic control system of FIG. 1;

FIG. 3 is a schematic diagram of a first pressure relief and relief mechanism of the hydraulic control system of FIG. 1;

FIG. 4 is a schematic diagram of a fifth reversing valve and a second pressure relief and relief mechanism of the hydraulic control system of FIG. 1; and

fig. 5 shows a schematic structural view of a second implement cylinder and a sixth directional valve of the hydraulic control system of fig. 1.

Reference numerals illustrate:

10. an oil inlet pipeline; 20. an oil return pipeline; 30. a pressurizing pipeline; 40. a pressure increasing valve; 41. a valve body; 42. a piston; 421. a first piston; 422. a second piston; 43. a high pressure chamber; 44. a low pressure chamber; 45. a first oil port; 46. a second oil port; 47. a rod cavity is arranged; 48. a sixth oil port; 50. a first unidirectional flow mechanism; 60. a second unidirectional flow mechanism; 70. a switching mechanism; 71. a third oil port; 72. a fourth oil port; 73. a fifth oil port; 74. a first control line; 75. a control spring; 76. a second control line; 80. a pressure relief pipeline; 90. a hydraulic lock; 100. a first hydraulic pump; 200. a first oil supply path; 300. an oil discharge oil path; 400. a hydraulic pressurization system; 500. a second reversing valve; 600. a third reversing valve; 700. a first execution cylinder; 800. the first pressure relief overflow mechanism; 801. a fourth reversing valve; 802. a first overflow valve; 900. a second oil supply passage; 1000. a second hydraulic pump; 1100. a fifth reversing valve; 1200. a second execution cylinder; 1300. a sixth reversing valve; 1400. the second pressure relief overflow mechanism; 1401. a seventh reversing valve; 1402. and a second relief valve.

Detailed Description

The following description of the embodiments of the present utility model will be made apparent and fully in view of the accompanying drawings, in which some, but not all embodiments of the utility model are shown. All other embodiments, which can be made by those skilled in the art based on the embodiments of the utility model without making any inventive effort, are intended to be within the scope of the utility model.

In the description of the present utility model, it should be noted that the directions or positional relationships indicated by the terms "center", "upper", "lower", "left", "right", "vertical", "horizontal", "inner", "outer", etc. are based on the directions or positional relationships shown in the drawings, are merely for convenience of describing the present utility model and simplifying the description, and do not indicate or imply that the devices or elements referred to must have a specific orientation, be configured and operated in a specific orientation, and thus should not be construed as limiting the present utility model. Furthermore, the terms "first," "second," and "third" are used for descriptive purposes only and are not to be construed as indicating or implying relative importance.

In the description of the present utility model, it should be noted that, unless explicitly specified and limited otherwise, the terms "mounted," "connected," and "connected" are to be construed broadly, and may be either fixedly connected, detachably connected, or integrally connected, for example; can be mechanically or electrically connected; can be directly connected or indirectly connected through an intermediate medium, and can be communication between two elements. The specific meaning of the above terms in the present utility model can be understood by those of ordinary skill in the art according to the specific circumstances.

In addition, the technical features of the different embodiments of the present utility model described below may be combined with each other as long as they do not collide with each other.

As shown in fig. 1 and 2, the embodiment of the hydraulic pressurization system of the present application includes an oil intake line 10, an oil return line 20, a pressurization line 30, a first one-way circulation mechanism 50, a second one-way circulation mechanism 60, and a switching mechanism 70. The respective structures are described in detail below.

As shown in fig. 1 and 2, the oil feed line 10 and the oil return line 20 are adapted to be connected to the implement cylinder, and the pressurizing line 30 is provided in parallel with the oil feed line 10. Specifically, one of the oil feed line 10 and the oil return line 20 is connected to a rod-less chamber of the execution cylinder, and the other is connected to a rod-less chamber of the execution cylinder. In this embodiment, since the rodless cavity of the execution cylinder needs to be pressurized, that is, the thrust of the execution cylinder is increased, the oil inlet pipe 10 is connected to the rodless cavity of the execution cylinder, and the oil return pipe 20 is connected to the rod cavity of the execution cylinder.

Of course, it will be appreciated by those skilled in the art that when the ram of the implement cylinder is retracted, the oil feed line 10 will also return oil and the oil return line 20 will also return oil.

In some embodiments, not shown, if pressurization of the rod cavity of the actuator cylinder is required, the oil inlet line 10 may also be connected to the rod cavity of the actuator cylinder, and correspondingly, the oil return line 20 may be connected to the rod-less cavity of the actuator cylinder.

As can be seen in conjunction with fig. 2, the pressurizing pipe 30 is disposed in parallel with the oil inlet pipe 10, and the pressurizing valve on the pressurizing pipe 30 can increase the pressure of the hydraulic oil without increasing the system pressure in the oil inlet pipe 10, and output the pressurized hydraulic oil to the actuating cylinder.

As shown in fig. 2, the pressure increasing valve 40 includes a valve body 41 and a piston 42 provided in the valve body 41. The piston 42 includes a first piston 421 and a second piston 422, the diameter of the first piston 421 being smaller than the diameter of the second piston 422. The piston 42 divides the interior of the valve body 41 into a high pressure chamber 43 located outside the first piston 421 and a low pressure chamber 44 located outside the second piston 422. The valve body 41 is provided with a first oil port 45 communicated with the high-pressure cavity 43 and a second oil port 46 communicated with the low-pressure cavity 44, and the first oil port 45 is connected with the pressurizing pipeline 30;

specifically, the first piston 421 and the second piston 422 are integrally connected by a connecting rod, that is, the first piston 421 and the second piston 422 move synchronously. Since the diameter of the first piston 421 is smaller than the diameter of the second piston 422, the inner cavity of the valve body 41 also suitably includes a small diameter section and a large diameter section, such that the inner cavity of the valve body 41 forms a "convex" structure.

The chamber located on the upper side of the first piston 421 in fig. 2 is a high pressure chamber 43, and the chamber located on the lower side of the second piston 422 is a low pressure chamber 44. As the piston 42 moves upward as a whole, the volume of the high-pressure chamber 43 decreases, and the volume of the low-pressure chamber 44 increases. As the piston 42 moves downward as a whole, the volume of the high-pressure chamber 43 increases, and the volume of the low-pressure chamber 44 decreases.

Further, when the piston 42 is moved downward as a whole, hydraulic oil can enter the high-pressure chamber 43 from the first oil port 45. When the piston 42 moves upward as a whole, hydraulic oil is discharged from the first oil port 45. Since the diameter of the first piston 421 is smaller than the diameter of the second piston 422, the hydraulic oil is pressurized at the time of discharge. The reciprocating up-and-down movement of the piston 42, i.e., the high-pressure chamber 43, continues to perform "oil suction-oil discharge", thereby achieving continuous pressurization.

As shown in fig. 2, the first and second one- way circulation mechanisms 50 and 60 are provided at the upper and downstream positions of the first oil port 45, respectively, and each of the first and second one- way circulation mechanisms 50 and 60 is adapted to circulate hydraulic oil in one way in a direction toward the actuator cylinder.

In the present embodiment, the upstream position and the downstream position refer to the upstream position and the downstream position of the first port 45 in the direction in which the hydraulic oil flows to the actuator cylinder. As will be appreciated by those skilled in the art in conjunction with fig. 2, when the piston 42 moves downward, a negative pressure is created in the high pressure chamber 43, hydraulic oil can flow through the first one-way flow mechanism 50, and the second one-way flow mechanism 60 is closed, so that hydraulic oil enters the high pressure chamber. When the piston 42 moves upward, the pressure in the high-pressure chamber 43 increases, the hydraulic oil can flow through the second one-way circulation mechanism 60, and the first one-way circulation mechanism 50 is closed, so that the pressurized hydraulic oil is delivered into the actuator cylinder while preventing the hydraulic oil from flowing back from the pressurizing pipe 30.

In addition, when pressurization is performed, the pressure in the rodless cavity of the execution cylinder enables the first unidirectional circulation mechanism 50 and the second unidirectional circulation mechanism 60 to be closed, so that the pressure maintaining effect is prevented.

Preferably, the first unidirectional flow mechanism 50 and the second unidirectional flow mechanism 60 are both unidirectional valves.

As shown in fig. 2, a switching mechanism 70 is connected to the pressure increasing valve 40, the switching mechanism 70 being adapted to communicate the second port 46 with the pressure increasing line 30 or to communicate the second port 46 with the return line 20. Specifically, when the second oil port 46 communicates with the oil return line 20, the low pressure chamber 44 is depressurized, the piston 42 moves downward, and hydraulic oil enters the high pressure chamber 43. When the second oil port 46 is communicated with the pressurizing pipeline 30, hydraulic oil is introduced into the low-pressure cavity 44, the piston 42 moves upwards, the pressure of the high-pressure cavity 43 is increased, and pressurized hydraulic oil is output. The switching mechanism 70 enables the reciprocating movement of the driving piston 42 by making the second oil port 46 communicate with the pressurizing line 30 and the return line 20 reciprocally, so that the hydraulic pressurizing system is continuously pressurized.

In summary, with the technical solution of the present embodiment, hydraulic oil is supplied from the oil inlet line 10 to the execution cylinder. Meanwhile, the pressurizing pipe 30 is provided with the pressurizing valve 40, when the switching mechanism 70 enables the second oil port 46 to be communicated with the oil return pipe 20, the low-pressure cavity 44 is depressurized, and hydraulic oil enters the high-pressure cavity 43 from the pressurizing pipe 30 through the first oil port 45. When the switching mechanism 70 causes the second port 46 to communicate with the pressurizing pipe 30, the low pressure chamber 44 is filled with oil, and the high pressure chamber 43 is compressed. Since the diameter of the first piston 421 is smaller than the diameter of the second piston 422, pressurized hydraulic oil is output from the first oil port 45 to the pressurizing line 30 and supplied to the actuator cylinder. The switching mechanism 70 drives the piston 42 to reciprocate by making the second oil port 46 communicate with the pressurizing line 30 and the oil return line 20 reciprocally, so as to realize continuous pressurizing. In the above structure, the system oil pressure in the oil inlet pipeline 10 does not need to be continuously increased, continuous pressurization is realized through the pressurization valve 40 on the pressurization pipeline 30, the system oil pressure is at a lower level, and the overflow heating value is small. Therefore, the technical scheme of the embodiment solves the defects that the system pressure is high and overflow heating is serious when the garbage compression box compresses garbage in the prior art.

As shown in fig. 2, the switching mechanism 70 is preferably a first reversing valve having a first position and a second position. The first reversing valve communicates the second port 46 with the boost line 30 when in the first position and communicates the second port 46 with the return line 20 when in the second position. The continuous reversing of the first reversing valve realizes the reciprocating communication between the second oil port 46 and the pressurizing pipeline 30 and the oil return pipeline 20.

As shown in fig. 1 and 2, in the technical solution of the present embodiment, a rod chamber 47 is formed in a space between a first piston 421 and a second piston 422, and the rod chamber 47 communicates with an oil return line 20 through a pressure release line 80. The first reversing valve is provided with a third oil port 71, a fourth oil port 72 and a fifth oil port 73. The third port 71 communicates with the rod chamber 47, the fourth port 72 communicates with the second port 46, and the fifth port 73 communicates with the pressurization piping 30. The third port 71 is blocked and the fourth port 72 is in communication with the fifth port 73 when the diverter valve is in the first position, and the fifth port 73 is blocked and the third port 71 is in communication with the fourth port 72 when the diverter valve is in the second position.

Specifically, as can be seen in FIG. 2, the cavity formed by the first piston 421 and the second piston 422 is the rod cavity 47 of the booster valve 40. The rod chamber 47 is connected to the return line 20 via a pressure relief line 80, i.e. the rod chamber 47 is always in a pressure relief state.

As can be seen from fig. 2, the first reversing valve is a two-position three-way reversing valve. The first position described above, i.e., the upper position of the first reversing valve in fig. 2. The second position described above, i.e. the lower position of the first reversing valve in fig. 2. The fifth port 73 is located upstream of the first unidirectional flow mechanism 50 at a position where it is connected to the pressurization line 30 through a line.

As will be appreciated by those skilled in the art in conjunction with fig. 2, the third port 71 is closed when the first diverter valve is in the up position. The hydraulic oil flows into the low pressure chamber 44 through the fifth port 73, the fourth port 72, and the second port 46, and the piston 42 rises. When the first reversing valve is in the down position, the fifth port 73 is closed, the low pressure chamber 44 is depressurized through the fourth port 72, the third port 71, the rod chamber 47 and the depressurization line 80, and the piston 42 moves downward.

It can be seen that in this embodiment, by controlling the reciprocating switching of the first reversing valve between the upper position and the lower position, the reciprocating movement of the piston 42 can be controlled, thereby realizing the continuous pressurization of the hydraulic oil.

As shown in fig. 2, in the technical solution of the embodiment, the valve body 41 is provided with a sixth oil port 48, and the sixth oil port 48 can be communicated with the high-pressure chamber 43 or the rod chamber 47 during the reciprocating movement of the first piston 421, or the sixth oil port 48 is closed by the first piston 421. One end of the first reversing valve is provided with a first control pipeline 74 and a control spring 75, the first control pipeline 74 is communicated with the sixth oil port 48, the other end of the first reversing valve is provided with a second control pipeline 76, and the second control pipeline 76 is communicated with the pressurizing pipeline 30.

Specifically, the sixth oil port 48 is provided in the middle of the small diameter section of the valve body 41. As will be appreciated by those skilled in the art in conjunction with fig. 2, when the first piston 421 is raised to the limit position, or is near the limit position, the sixth port 48 communicates with the rod chamber 47. During the descent of the first piston 421, the first piston 421 passes through the sixth oil port 48 and closes the sixth oil port 48. When the first piston 421 descends to or near the extreme position, the sixth oil port 48 communicates with the high-pressure chamber 43.

Further, the first reversing valve is a hydraulic control reversing valve, the first control pipeline 74 and the control spring 75 are located at the upper end of the first reversing valve, and the second control pipeline 76 is located at the lower end of the first reversing valve. The upper and lower positions of the first directional valve are determined by the pressure in the first control line 74, the pressure in the second control line 76, and the elastic force of the control spring 75.

As will be appreciated by those skilled in the art in conjunction with fig. 2, when the piston 42 is moved up to the limit position, i.e., after the pressure build-up valve 40 has been exhausted, the first control line 74 communicates with the rod chamber 47, i.e., the first control line 74 is in a pressure relief state, and the pressure in the second control line 76 overcomes the spring force of the control spring 75, such that the first directional valve is in a low position. At this time, the fifth oil port 73 is closed, the low pressure chamber 44 is depressurized through the fourth oil port 72, the third oil port 71, the rod chamber 47 and the depressurization line 80, at this time, the piston 42 moves downward, and hydraulic oil enters the high pressure chamber 43.

When the piston 42 moves down to the limit position, the first control line 74 communicates with the high pressure chamber 43. At this time, the pressure in the first control line 74 is equal to the pressure in the second control line 76, and the first directional valve is switched to the upper position by the elastic force of the control spring 75. At this time, the third port 71 is closed, hydraulic oil flows into the low pressure chamber 44 through the fifth port 73, the fourth port 72 and the second port 46, and the piston 42 is lifted up to realize pressurization and oil discharge.

Therefore, in the process of reciprocating up and down movement of the piston 42, the first reversing valve automatically switches between the up and down positions, so that the pressure increasing valve 40 continuously increases pressure.

Of course, the first directional valve may also be provided as an electromagnetic directional valve.

The oil inlet line 10 and the oil return line 20 are provided with a hydraulic lock 90.

As shown in fig. 1, the present application also provides a hydraulic control system according to an embodiment of the hydraulic control system of the present application, including the first hydraulic pump 100, the first oil supply line 200, the oil discharge line 300, the hydraulic pressurization system 400 described above, and the first implement cylinder 700. Wherein the first hydraulic pump 100 communicates with the first oil supply passage 200 and is adapted to supply oil to the first oil supply passage 200. The oil discharge passage 300 is adapted to communicate with an external oil tank. The oil inlet line 10 of the hydraulic pressure boosting system 400 communicates with the first oil supply line 200 or the oil discharge line 300 through the second directional valve 500, and the oil return line 20 of the hydraulic pressure boosting system 400 communicates with the first oil supply line 200 or the oil discharge line 300 through the third directional valve 600. The oil feed line 10 and the oil return line 20 are respectively communicated with a rodless chamber and a rod-containing chamber of the first implement cylinder 700.

In the hydraulic control system of the present embodiment, since the hydraulic pressure boosting system 400 is provided, a large system pressure is not required in the first supply oil passage 200, that is, the first hydraulic pump 100 is selected as a small flow pump.

As shown in fig. 1 and 2, the second reversing valve 500 and the third reversing valve 600 are two-position four-way reversing valves. It will be appreciated by those skilled in the art that when both the second reversing valve 500 and the third reversing valve 600 are energized, both are in the right position, at which time the oil feed line 10 feeds oil and the oil return line 20 returns oil. When both the second reversing valve 500 and the third reversing valve 600 are powered off, both are in the left position, and at this time, the oil inlet pipeline 10 returns oil, and the oil return pipeline 20 returns oil.

As shown in fig. 1 and 3, in the technical solution of the present embodiment, the hydraulic control system further includes a first pressure relief and overflow mechanism 800. The first pressure relief and relief mechanism 800 includes a fourth reversing valve 801 and a first relief valve 802 that are disposed in parallel, the fourth reversing valve 801 being adapted to connect or disconnect the first oil supply passage 200 and the oil discharge passage 300, and an inlet and an outlet of the first relief valve 802 being respectively connected to the first oil supply passage 200 and the oil discharge passage 300.

As can be seen in conjunction with fig. 3, first spill valve 802 may set the system pressure in first supply oil passage 200. When the oil pressure is greater than the set pressure, hydraulic oil overflows from the first relief valve 802. Since the hydraulic pressure boosting system 400 is provided in the hydraulic system, the set pressure of the first relief valve 802 can be small and the heat generation amount can be small.

As can be seen in connection with fig. 3, the fourth reversing valve 801 is a two-position four-way reversing valve. When the fourth switching valve 801 is energized, it is operated in the right position, at which time the first supply oil passage 200 and the discharge oil passage 300 are disconnected, and the first hydraulic pump 100 can supply oil to the first implement cylinder 700. When the fourth switching valve 801 is deenergized, it operates in the left position, at which the first oil supply passage 200 and the oil discharge passage 300 are communicated, and the first oil supply passage 200 is discharged.

As shown in fig. 1, in the technical solution of the present embodiment, the hydraulic control system further includes a second oil supply line 900, a second hydraulic pump 1000, and a second execution cylinder 1200. Wherein the second hydraulic pump 1000 communicates with the first oil supply passage 200 or the second oil supply passage 900 through the fifth directional valve 1100. The second actuating cylinder 1200 communicates with the second oil supply passage 900 and the oil discharge passage 300 through the sixth directional valve 1300.

Specifically, second hydraulic pump 1000 is a high flow pump and, as can be seen in conjunction with FIG. 4, fifth reversing valve 1100 is a two-position, four-way reversing valve. When the fifth switching valve 1100 is in the power-on state, it is operated in the right position, and the second hydraulic pump 1000 is in communication with the first supply oil path 200, that is, supplies oil to the first implement cylinder 700. When the fifth switching valve 1100 is in the power-off state, it is operated in the left position, and the second hydraulic pump 1000 is in communication with the second oil supply passage 900, that is, supplies oil to the second execution cylinder 1200.

In the present embodiment, in addition to the oil supply method of the small-flow pump (the first hydraulic pump 100) and the hydraulic pressure increasing system 400, the first actuator cylinder 700 may be directly supplied with oil by a large-flow pump (the second hydraulic pump 1000).

As can be seen in conjunction with fig. 5, the sixth reversing valve 1300 is a three-position four-way reversing valve. When the left side of the sixth reversing valve 1300 is powered, the sixth reversing valve 1300 is operated at the left position, and the rod cavity of the second execution cylinder 1200 is filled with oil, and the rod cavity is not filled with oil. When the right side of the sixth reversing valve 1300 is powered, the sixth reversing valve 1300 is operated at the right position, and at this time, the oil is returned from the rod cavity of the second execution cylinder 1200, and the oil is fed from the rodless cavity.

As shown in fig. 4, in the technical solution of the present embodiment, the hydraulic control system further includes a second relief and overflow mechanism 1400, and the second relief and overflow mechanism 1400 includes a seventh reversing valve 1401 and a second overflow valve 1402 that are disposed in parallel. The seventh reversing valve 1401 is adapted to connect or disconnect the second oil supply oil passage 900 and the oil discharge oil passage 300, and an inlet and an outlet of the second relief valve 1402 are respectively connected to the second oil supply oil passage 900 and the oil discharge oil passage 300.

As can be seen in connection with fig. 4, the second spill valve 1402 may set the system pressure in the second supply line 900. When the oil pressure is greater than the set pressure, hydraulic oil overflows from the second relief valve 1402.

As can be seen in connection with fig. 3, the seventh reversing valve 1401 is a two-position four-way reversing valve. When the seventh switching valve 1401 is energized, it operates in the left position, at which time the second supply oil path 900 and the discharge oil path 300 are disconnected, and the second hydraulic pump 1000 can supply oil to the second execution cylinder 1200. When the seventh switching valve 1401 is deenergized, it operates in the right position, at which the second oil supply passage 900 and the oil discharge passage 300 are communicated, and the second oil supply passage 900 is discharged.

The application also provides a garbage compression box, and an embodiment of the garbage compression box according to the application comprises the hydraulic control system.

Further, the garbage compression box further comprises a box body, a pushing head for compressing garbage and a feeding mechanism. The first actuating cylinder 700 is connected to the pusher, and the second actuating cylinder 1200 is connected to the feeding mechanism.

When the pushing head compresses garbage, a small flow pump (the first hydraulic pump 100) is used for supplying oil, and the pressure of the pushing head is increased by continuously pressurizing a pressurizing cylinder in the hydraulic pressurizing system 400, meanwhile, the system pressure of the first oil supply oil way 200 is not increased, and overflow heating of the hydraulic system during pushing head compression is reduced.

When the hopper of the feeding mechanism is closed and falls to the ground, the seventh reversing valve 1401 is powered off, and the second oil supply path 900 is unloaded. The closing and the landing actions are completed by means of the gravity of the hopper, so that the working time of the hydraulic system is shortened, the energy consumption is saved, and the heating of the hydraulic system is reduced.

It should be noted that, any occasion where thrust is required in other fields may use the hydraulic pressurization system and the hydraulic control system, and is not limited to application in the garbage compression box. The present embodiment is not to be construed as limiting the application scenarios of the hydraulic compression system and the hydraulic control system described above.

According to the above description, the patent application has the following advantages:

1. when the pushing head of the garbage compression box compresses at a low speed, the small flow is used for maintaining pressure, and the overflow heating of the system is less;

2. the pushing head of the garbage compression box is pressurized by the pressurizing cylinder, so that the system setting pressure is low, the system energy consumption and power consumption are low, and the heat productivity is low;

3. when the feeding hopper of the feeding mechanism of the garbage compression box is closed and falls to the ground, the action is finished by means of gravity, so that the working time of the system is shortened, the energy consumption is saved, and the heating of the system is reduced.

It is apparent that the above examples are given by way of illustration only and are not limiting of the embodiments. Other variations or modifications of the above teachings will be apparent to those of ordinary skill in the art. It is not necessary here nor is it exhaustive of all embodiments. While still being apparent from variations or modifications that may be made by those skilled in the art are within the scope of the utility model.

Claims (10)

1. A hydraulic boost system, comprising:

the oil inlet pipeline (10) and the oil return pipeline (20) are suitable for being connected with the execution oil cylinder;

the pressurizing pipeline (30) is connected with the oil inlet pipeline (10) in parallel;

a pressure increasing valve (40) comprising a valve body (41) and a piston (42) arranged in the valve body (41), wherein the piston (42) comprises a first piston (421) and a second piston (422), the diameter of the first piston (421) is smaller than that of the second piston (422), the piston (42) divides the valve body (41) into a high-pressure cavity (43) positioned outside the first piston (421) and a low-pressure cavity (44) positioned outside the second piston (422), a first oil port (45) communicated with the high-pressure cavity (43) and a second oil port (46) communicated with the low-pressure cavity (44) are arranged on the valve body (41), and the first oil port (45) is connected with a pressure increasing pipeline (30);

the first unidirectional circulation mechanism (50) and the second unidirectional circulation mechanism (60) are respectively arranged at the upstream position and the downstream position of the first oil port (45), and the first unidirectional circulation mechanism (50) and the second unidirectional circulation mechanism (60) are both suitable for unidirectional circulation of hydraulic oil along the direction towards the execution oil cylinder;

and a switching mechanism (70) connected with the pressure increasing valve (40), wherein the switching mechanism (70) is suitable for enabling the second oil port (46) to be communicated with the pressure increasing pipeline (30) or enabling the second oil port (46) to be communicated with the oil return pipeline (20).

2. The hydraulic boost system of claim 1 wherein the switching mechanism (70) is a first reversing valve having a first position and a second position, the first reversing valve placing the second port (46) in communication with the boost line (30) when in the first position and placing the second port (46) in communication with the return line (20) when in the second position.

3. The hydraulic boost system according to claim 2, characterized in that a rod chamber (47) is formed in a space between the first piston (421) and the second piston (422), the rod chamber (47) is communicated with the oil return line (20) through a relief line (80), a third oil port (71), a fourth oil port (72) and a fifth oil port (73) are provided on the first reversing valve, the third oil port (71) is communicated with the rod chamber (47), the fourth oil port (72) is communicated with the second oil port (46), the fifth oil port (73) is communicated with the boost line (30), the third oil port (71) is blocked when the reversing valve is in the first position, and the fourth oil port (72) is communicated with the fifth oil port (73), and the fifth oil port (73) is blocked when the first reversing valve is in the second position, and the third oil port (71) is communicated with the fourth oil port (72).

4. A hydraulic charging system according to claim 3, characterized in that the valve body (41) is provided with a sixth oil port (48), the sixth oil port (48) being capable of communicating with the high-pressure chamber (43) or the rod chamber (47) during the reciprocating movement of the first piston (421), or the sixth oil port (48) being closed by the first piston (421),

one end of the first reversing valve is provided with a first control pipeline (74) and a control spring (75), the first control pipeline (74) is communicated with the sixth oil port (48), the other end of the first reversing valve is provided with a second control pipeline (76), and the second control pipeline (76) is communicated with the pressurizing pipeline (30).

5. A hydraulic charging system according to claim 3, characterized in that the oil inlet line (10) and the oil return line (20) are provided with hydraulic locks (90).

6. A hydraulic control system, comprising:

a first hydraulic pump (100);

a first oil supply passage (200), the first hydraulic pump (100) being in communication with the first oil supply passage (200);

an oil discharge path (300) adapted to communicate with an external oil tank;

the hydraulic boosting system (400) according to any one of claims 1 to 5, the oil inlet line (10) being in communication with the first oil supply line (200) or the oil discharge line (300) through a second reversing valve (500), the oil return line (20) being in communication with the first oil supply line (200) or the oil discharge line (300) through a third reversing valve (600);

the oil inlet pipeline (10) and the oil return pipeline (20) are respectively communicated with a rodless cavity and a rod cavity of the first execution oil cylinder (700).

7. The hydraulic control system according to claim 6, further comprising a first pressure relief and relief mechanism (800), the first pressure relief and relief mechanism (800) comprising a fourth reversing valve (801) and a first relief valve (802) arranged in parallel, the fourth reversing valve (801) being adapted to connect and disconnect a first oil supply circuit (200) and an oil discharge circuit (300), an inlet and an outlet of the first relief valve (802) being in communication with the first oil supply circuit (200) and the oil discharge circuit (300), respectively.

8. The hydraulic control system of claim 6, further comprising:

a second oil supply passage (900);

a second hydraulic pump (1000), the second hydraulic pump (1000) being in communication with the first oil supply passage (200) or the second oil supply passage (900) through a fifth reversing valve (1100);

the second execution oil cylinder (1200) is communicated with the second oil supply oil path (900) and the oil discharge oil path (300) through a sixth reversing valve (1300).

9. The hydraulic control system according to claim 8, further comprising a second relief and relief mechanism (1400), the second relief and relief mechanism (1400) comprising a seventh reversing valve (1401) and a second relief valve (1402) arranged in parallel, the seventh reversing valve (1401) being adapted to connect and disconnect a second oil supply circuit (900) and an oil discharge circuit (300), an inlet and an outlet of the second relief valve (1402) being in communication with the second oil supply circuit (900) and the oil discharge circuit (300), respectively.

10. A waste bin comprising a hydraulic control system as claimed in any one of claims 6 to 9.

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