A hydraulic system for a skid steer loader and a skid steer loader

Abstract

The utility model discloses a hydraulic system of slip excavating loader and slip excavating loader, and the hydraulic system includes: the import Pw of excavating valve and the import Pz of loading valve are connected to the export P1 of gear series pump, the import P4 of confluence switch valve group is connected to the export P2 of gear series pump, the import P5 of loading valve is connected to the working port A of confluence switch valve group, and the working port of loading valve is connected to implement respectively, and confluence switch valve group includes reversing valve no.

Description

Technical Field

[0001] This utility model belongs to the technical field of skid steer excavator loaders, specifically relating to a hydraulic system for a skid steer excavator loader and a skid steer excavator loader. Background Technology

[0002] With technological advancements, an increasing number of machinery tools are being used in daily construction, especially backhoe loaders. Backhoe loaders are engineering machines that integrate loading and excavation, and are widely used in municipal engineering, construction, agriculture, and disaster relief due to their maneuverability and versatility. Their core value lies in adapting to different operational scenarios by quickly changing different hydraulic tools (such as buckets, breakers, sweepers, drills, snow blowers, etc.). In existing technologies, when using high-pressure tools (such as breakers), most of the flow must overflow through the relief valve, wasting energy as heat. This leads to severe system overheating, a surge in fuel consumption, and even shutdown due to excessively high oil temperature, preventing prolonged operation. Furthermore, existing technologies use electronically controlled variable pumps to supply pressurized oil, resulting in extremely high operating costs, complex technology, high requirements for oil cleanliness, and difficult maintenance. The high cost makes them unsuitable for price-sensitive and demanding small- to medium-sized markets. Utility Model Content

[0003] To address the shortcomings of existing technologies, this utility model provides a hydraulic system for a skid steer excavator loader and a skid steer excavator loader, which can switch between "high flow" and "high pressure" operating conditions according to the needs of the machine, thereby reducing waste, lowering energy consumption, and reducing manufacturing and operating costs.

[0004] To achieve the above objectives, the technical solution adopted by this utility model is as follows: In a first aspect, a hydraulic system for a skid steer excavator loader is provided, comprising: a gear cascade pump, the outlet P1 of which is connected to the inlet Pw of an excavating valve and the inlet Pz of a loading valve; the outlet P2 of which is connected to the inlet P4 of a confluence switching valve assembly; the working port A of the confluence switching valve assembly is connected to the inlet P5 of the loading valve; the working ports A3 and B3 of the loading valve are respectively connected to implements; the confluence switching valve assembly includes a first directional valve, the inlet of which is connected to the inlet P4 of the confluence switching valve assembly, the inlet of a second relief valve, and the inlet of a check valve; the outlets of the first directional valve and the second relief valve are respectively connected to the return port T of the confluence switching valve assembly; the outlet of the check valve is connected to the working port A of the confluence switching valve assembly; a relay Y1 of the first directional valve is electrically connected to a controller; and a rocker switch for energizing or de-energizing the relay Y1 of the first directional valve is electrically connected to the controller.

[0005] Furthermore, the oil return port T1 of the excavation valve, the oil return port T2 of the loading valve, and the oil return port T of the confluence switching valve group are respectively connected to the oil tank.

[0006] Furthermore, the reversing valve is a two-position, two-way solenoid reversing valve.

[0007] Furthermore, the loading valve includes a second directional control valve, the inlet of which is connected to the inlet Pz and the inlet P5 of the loading valve respectively; the working port of the second directional control valve is connected to the working port A3 and the working port B3 of the loading valve respectively; and the return port of the second directional control valve is connected to the return port T2 of the loading valve.

[0008] Furthermore, the second directional valve is a three-position six-way solenoid directional valve.

[0009] Furthermore, relays Y2 and Y3 of the second reversing valve are electrically connected to the controller; the handle roller used to energize or de-energize relays Y2 and Y3 of the second reversing valve is electrically connected to the controller.

[0010] Furthermore, the loading valve also includes an overflow valve located in the return oil line inside the loading valve.

[0011] Furthermore, the implements include a bucket, a breaker, hydraulic shears, a sweeper, a ground sweeper, a blower, a drill, and a snow blower.

[0012] In a second aspect, a skid steer excavator loader is provided, the skid steer excavator loader being equipped with the skid steer excavator loader hydraulic system described in the first aspect.

[0013] Compared with the prior art, the beneficial effects achieved by this utility model are as follows: This utility model connects the outlet P1 of the gear cascade pump to the inlet Pw of the excavating valve and the inlet Pz of the loading valve; the outlet P2 of the gear cascade pump is connected to the inlet P4 of the confluence switching valve group; the working port A of the confluence switching valve group is connected to the inlet P5 of the loading valve; the working ports A3 and B3 of the loading valve are respectively connected to the implement; the confluence switching valve group includes a reversing valve, the inlet of which is connected to the inlet P4 and the overflow of the confluence switching valve group. The inlet of valve two and the inlet of the check valve; the outlet of the reversing valve one and the outlet of the overflow valve two are respectively connected to the return port T of the confluence switching valve group; the outlet of the check valve is connected to the working port A of the confluence switching valve group; the relay Y1 of the reversing valve one is electrically connected to the controller; the rocker switch used to energize or de-energize the relay Y1 of the reversing valve one is electrically connected to the controller; it can switch between "high flow" and "high pressure" working conditions according to the needs of the machine, thereby reducing waste, reducing energy consumption, and reducing manufacturing and use costs. Attached Figure Description

[0014] Figure 1 This is a schematic diagram of the hydraulic system of a skid steer excavator loader provided in an embodiment of this utility model; In the diagram: 1. Oil tank; 2. Confluence switching valve group; 3. Directional valve one; 4. Gear cascade pump; 5. Travel pump; 6. Excavating valve; 7. Loading valve; 8. Tool; 9. Handle roller; 10. Rocker switch; 11. Overflow valve one; 12. Directional valve two; 13. Controller; 14. Overflow valve two; 15. Check valve. Detailed Implementation

[0015] The present invention will be further described below with reference to the accompanying drawings. The following embodiments are only used to more clearly illustrate the technical solution of the present invention, and should not be used to limit the scope of protection of the present invention.

[0016] Example 1 like Figure 1 As shown, a hydraulic system for a skid steer excavator loader includes: an oil tank 1, a confluence switching valve group 2, a first directional valve 3 (a two-position two-way solenoid directional valve), a gear pump 4, a travel pump 5, an excavating valve 6, a loading valve 7, a tool 8, a handle roller 9, a rocker switch 10, a first relief valve 11, a second directional valve 12 (a three-position six-way solenoid directional valve), a controller 13, a second relief valve 14, and a check valve 15.

[0017] The outlet P1 of the gear cascade pump 4 is connected to the inlet Pw of the excavation valve 6 and the inlet Pz of the loading valve 7; the outlet P2 of the gear cascade pump 4 is connected to the inlet P4 of the confluence switching valve group 2; the working port A of the confluence switching valve group 2 is connected to the inlet P5 of the loading valve 7; the working ports A3 and B3 of the loading valve 7 are respectively connected to the implement 8.

[0018] The confluence switching valve group 2 includes a reversing valve 3. The inlet of the reversing valve 3 is connected to the inlet P4 of the confluence switching valve group 2, the inlet of the relief valve 14, and the inlet of the check valve 15. The outlets of the reversing valve 3 and the relief valve 14 are connected to the return port T of the confluence switching valve group 2. The outlet of the check valve 15 is connected to the working port A of the confluence switching valve group 2.

[0019] The relay Y1 of the reversing valve 3 is electrically connected to the controller 13.

[0020] The rocker switch 10, used to energize or de-energize the relay Y1 of the reversing valve 3, is electrically connected to the controller 13.

[0021] The return port T1 of the excavation valve 6, the return port T2 of the loading valve 7, and the return port T of the confluence switching valve group 2 are respectively connected to the oil tank 1.

[0022] The loading valve 7 includes a second directional valve 12 and a first overflow valve 11 installed in the return oil line inside the loading valve 7. The inlet of the second directional valve 12 is connected to the inlet Pz and the inlet P5 of the loading valve 7, respectively. The working port of the second directional valve 12 is connected to the working port A3 and the working port B3 of the loading valve 7, respectively. The return oil port of the second directional valve 12 is connected to the return oil port T2 of the loading valve 7.

[0023] Relays Y2 and Y3 of directional valve 12 are electrically connected to controller 13; the handle roller 9, used to energize or de-energize relays Y2 and Y3 of directional valve 12, is electrically connected to controller 13.

[0024] The traveling pump 5 is connected to the gear cascade pump 4. The outlet E of the traveling pump 5 is connected to the outlet P3 of the gear cascade pump 4; the suction port of the gear cascade pump 4 is connected to the oil tank 1. The gear cascade pump 4 includes gear pump one, gear pump two, and gear pump three. The outlet of gear pump one is connected to the outlet P1 of the gear cascade pump 4, the outlet of gear pump two is connected to the outlet P2 of the gear cascade pump 4, and the outlet of gear pump three is connected to the outlet P3 of the gear cascade pump 4. The suction ports of gear pump one, gear pump two, and gear pump three are connected to the oil tank 1.

[0025] The controller 13 is used to control the opening and closing of the first reversing valve 3. The rocker switch 10 is used to send selection commands to the controller 13. The controller 13 can switch the system to "high flow" or "high pressure" according to the selected command. The controller 13 is also used to control the opening and closing of the second reversing valve 12. The handle roller 9 is used to send selection commands to the controller 13. The controller 13 can realize the action of the machine 8 according to the selected command.

[0026] The implement 8 refers to the implement components of construction machinery, which may include buckets, breakers, hydraulic shears, sweepers, sweepers, blowers, drills, and snow blowers, etc.

[0027] When the machine needs to operate in "high flow" mode, the operator operates the rocker switch 10 to energize relay Y1 of directional valve 3 in the confluence switching valve group 2. This connects inlet P4 of the confluence switching valve group 2 to working port A through check valve 15, thereby connecting to inlet P5 of loading valve 7. At this time, the output flow rate is the product of the rotational speed of gear pump 4 and the displacement of gear pump 1 and gear pump 2 in gear pump 4. The maximum pressure of the output hydraulic oil is controlled by overflow valve 14 in the confluence switching valve group 2. At this time, the operator operates the handle roller 9 to control relays Y2 and Y3 of directional valve 12 in loading valve 7, connecting the oil circuit of loading valve 7 to tool 8, thus initiating the action of tool 8.

[0028] When the machine needs to operate in "high pressure" mode, the operator operates the rocker switch 10 to de-energize the relay Y1 of the reversing valve 3 in the confluence switching valve group 2, so that the inlet P4 of the confluence switching valve group 2 is connected to the oil tank 1, and the gear pump 2 in the gear cascade pump 4 is unloaded. At this time, the output flow rate is the product of the rotational speed of the gear cascade pump 4 and the displacement of the gear pump 1 in the gear cascade pump 4. The maximum output pressure at this time is controlled by the overflow valve 11 in the loading valve 7.

[0029] At this time, the operator operates the handle roller 9 to control the relays Y2 and Y3 of the reversing valve 12 in the loading valve 7, so that the oil circuit of the loading valve 7 is connected to the tool 8, and the tool 8 is activated.

[0030] This invention achieves switching between "high flow rate" and "high pressure" modes through a gear-driven pump and a separately configured confluence switching valve assembly, meeting the needs of different implements. It provides precise and efficient power to implements requiring high impact force, such as hydraulic breakers and hydraulic shears, avoiding energy waste and heat generation issues associated with high flow rates. It also provides ample flow to implements requiring high flow rates but not high pressure, such as sweepers, blowers, and tilting buckets, significantly improving work efficiency. Switching between "high pressure" and "high flow rate" modes allows each implement to perform at its optimal level.

[0031] This utility model achieves instantaneous merging and switching, seamlessly connecting different operating conditions. It also reduces costs: avoiding the increased initial costs associated with excessively large-displacement electronically controlled variable pumps in pursuit of high performance. Furthermore, it lowers long-term fuel and maintenance costs. Increased equipment efficiency means shorter time required for operators to complete the same workload, reducing labor intensity. Simultaneously, reduced heat generation in the hydraulic system lowers the heat load on the operator's cab, improving operator comfort and safety.

[0032] Example 2 Based on the skid steer excavator hydraulic system described in Embodiment 1, this embodiment provides a skid steer excavator loader, which is equipped with the skid steer excavator hydraulic system described in Embodiment 1.

[0033] The above description is only a preferred embodiment of the present utility model. It should be noted that for those skilled in the art, several improvements and modifications can be made without departing from the technical principles of the present utility model, and these improvements and modifications should also be considered within the protection scope of the present utility model.

Claims

1. A hydraulic system for a skid steer loader, comprising: include: Gear cascade pump (4), the outlet P1 of gear cascade pump (4) is connected to the inlet Pw of excavation valve (6) and the inlet Pz of loading valve (7); the outlet P2 of gear cascade pump (4) is connected to the inlet P4 of confluence switching valve group (2); the working port A of confluence switching valve group (2) is connected to the inlet P5 of loading valve (7); the working port A3 and working port B3 of loading valve (7) are respectively connected to the tool (8); The merging switching valve group (2) includes a reversing valve one (3), the inlet of the reversing valve one (3) is connected to the inlet P4 of the merging switching valve group (2), the inlet of the overflow valve two (14), and the inlet of the check valve (15); the outlet of the reversing valve one (3) and the outlet of the overflow valve two (14) are connected to the return port T of the merging switching valve group (2); the outlet of the check valve (15) is connected to the working port A of the merging switching valve group (2). The relay Y1 of the reversing valve (3) is electrically connected to the controller (13); The rocker switch (10) used to energize or de-energize the relay Y1 of the reversing valve (3) is electrically connected to the controller (13).

2. The hydraulic system for a skid steer excavator loader according to claim 1, characterized in that, The oil return port T1 of the excavation valve (6), the oil return port T2 of the loading valve (7), and the oil return port T of the confluence switching valve group (2) are respectively connected to the oil tank (1).

3. The hydraulic system for a skid steer excavator loader according to claim 1, characterized in that, The reversing valve (3) is a two-position two-way solenoid reversing valve.

4. The hydraulic system for a skid steer excavator loader according to claim 1, characterized in that, The loading valve (7) includes a second directional valve (12), the inlet of which is connected to the inlet Pz and the inlet P5 of the loading valve (7) respectively; the working port of the second directional valve (12) is connected to the working port A3 and the working port B3 of the loading valve (7) respectively; and the return port of the second directional valve (12) is connected to the return port T2 of the loading valve (7).

5. The hydraulic system for a skid steer excavator loader according to claim 4, characterized in that, The second reversing valve (12) is a three-position six-way solenoid reversing valve.

6. The hydraulic system for a skid steer excavator loader according to claim 4, characterized in that, The relays Y2 and Y3 of the second reversing valve (12) are electrically connected to the controller (13); The handle roller (9) used to energize or de-energize relays Y2 and Y3 of the reversing valve (12) is electrically connected to the controller (13).

7. The hydraulic system for a skid steer excavator loader according to claim 1, characterized in that, The loading valve (7) also includes an overflow valve (11) installed in the return oil line inside the loading valve (7).

8. The hydraulic system for a skid steer excavator loader according to claim 1, characterized in that, The equipment includes a bucket, a breaker, hydraulic shears, a sweeper, a sweeper, a blower, a drill, and a snow blower.

9. A skid steer excavator loader, characterized in that, The skid steer excavator loader is equipped with the skid steer excavator loader hydraulic system as described in any one of claims 1 to 8.

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