Power head motor reliability test hydraulic system and control method

Abstract

The invention provides a power head motor reliability test hydraulic system and a control method.The test hydraulic system comprises a first oil pump set and a second oil pump set, the first oil pump set is connected with a test board motor through a first reversing valve, and the second oil pump set is used for being connected with a tested motor; a second reversing valve is arranged between the second oil pump group and the tested motor; the testboard motor and the tested motor are in driving connection with each other; a third overflow valve, a third hydraulic control one-way valve and a third electromagnetic valve are arranged on a backpressure oil return path of the test bench motor; the third overflow valve and the third hydraulic control one-way valve are arranged in parallel, the third electromagnetic valve is connected with the far-conducting end of the third hydraulic control one-way valve, and when the third electromagnetic valve loses power, the back pressure torque of the motor of the test board is set through the third overflow valve; when the third electromagnetic valve is electrified, the motor of the test bench is unloaded; the first reversing valve and the second reversing valve are reversing valves with meso-position functions; according to the invention, the load condition of the power head motor under severe working conditions can be simulated.

Description

Technical Field

[0001] The present invention relates to the technical field of engineering machinery hydraulics, and in particular to a hydraulic system and a control method for reliability testing of a power head motor. Background Art

[0002] A rotary drilling rig is a construction tool suitable for drilling holes during the construction foundation process. When constructing in soil layers, sand layers, dense rock layers and other strata, as the drill tool advances, the drill tool load gradually and steadily increases. The operating condition of the rotary drilling rig power head motor used to drive the drill tool changes relatively stably and will not cause impact.

[0003] However, in the actual construction process, unstable strata are often encountered, such as pebble layers and rock strata with obvious cracks. In these strata, the operating load of the rotary drilling rig power head motor changes significantly, causing certain damage to the motor.

[0004] After a single drilling by the rotary drilling rig is completed, the debris and rocks are packed inside the drill tool. After the drill tool is lifted to the hole mouth, the power head is generally switched back and forth rapidly to use the relative inertia force to unload the debris or rocks in the drill tool.

[0005] In addition, due to the heavy cumulative weight of the drill tools, slag and drill rods, when the drill tools, slag and drill rods are swung, the cumulative weight will generate a huge inertial force and then impact the power head. This inertial force is transmitted to the power head motor, and the power head motor is subjected to short-term and high-impact alternating impacts, causing certain damage to the motor. Therefore, to measure the reliability of the power head motor, especially for new motors or newly developed motors, it is necessary to simulate the above working conditions.

[0006] Conducting reliability tests on a test bench simulating the harsh operating conditions of a rotary drilling rig can greatly shorten the application verification time of the power head motor.

[0007] Therefore, there is an urgent need for a hydraulic system and control method for reliability testing of a power head motor, which can simulate the load conditions of the power head motor of a rotary drilling rig under harsh operating conditions, so as to test the reliability of the power head motor and thus shorten the application verification time of the power head motor. Summary of the invention

[0008] The purpose of the present invention is to provide a hydraulic system and control method for reliability testing of a power head motor, aiming to solve the technical problem that it is difficult to simulate the operating load of the power head motor under complex working conditions using traditional testing methods.

[0009] To achieve the above objectives, in a first aspect, the present invention provides a hydraulic system for reliability testing of a power head motor. It comprises a first oil pump group and a second oil pump group, wherein the first oil pump group is connected to the test bench motor through a first reversing valve, the second oil pump group is used to be connected to the motor under test, and a second reversing valve is further provided between the second oil pump group and the motor under test; the test bench motor and the motor under test are mutually drivingly connected; A third relief valve, a third hydraulically controlled one-way valve and a third solenoid valve are provided on the back pressure return oil line of the test bench motor, which are used to control and adjust the back pressure torque of the test bench motor; The third relief valve and the third hydraulically controlled one-way valve are arranged in parallel, and the third solenoid valve is connected to the end away from the conduction end of the third hydraulically controlled one-way valve. When the third solenoid valve loses power, the back pressure torque of the test bench motor is set by the third relief valve; when the third solenoid valve is energized, the test bench motor is unloaded through the third hydraulically controlled one-way valve and the third solenoid valve in sequence; by alternately controlling the power on and off of the third solenoid valve, the return oil back pressure and back pressure torque of the test bench motor are changed to obtain the alternating operating load of the motor under test; The first reversing valve and the second reversing valve are both reversing valves with a neutral position function; the first reversing valve and the second reversing valve are switched to corresponding working positions by control to simulate the forward and reverse rotation of the power head motor to quickly switch and unload soil.

[0010] As a further improvement of the above solution, a first relief valve, a first hydraulically controlled one-way valve and a first solenoid valve are provided between the first oil pump group and the first reversing valve, for controlling and adjusting the operating pressure of the first oil pump group; The first relief valve and the first hydraulically controlled one-way valve are arranged in parallel, and the first solenoid valve is connected to the end away from the conduction end of the first hydraulically controlled one-way valve; When the first solenoid valve is energized, the first hydraulically controlled one-way valve is closed through the first solenoid valve, and the operating pressure of the first oil pump group is set by the first overflow valve; when the first solenoid valve loses power, the hydraulic oil of the first oil pump group returns to the oil tank through the first hydraulically controlled one-way valve and the first solenoid valve in sequence.

[0011] As a further improvement of the above solution, a second relief valve, a second hydraulically controlled one-way valve and a second solenoid valve are provided between the second oil pump group and the second reversing valve, for controlling and adjusting the operating pressure of the second oil pump group; The second overflow valve and the second hydraulically controlled one-way valve are arranged in parallel, and the second solenoid valve is connected to the end away from the conduction end of the second hydraulically controlled one-way valve; When the second solenoid valve loses power, the second hydraulically controlled one-way valve is closed by the second solenoid valve, and the operating pressure of the second oil pump group is set by the second overflow valve; when the second solenoid valve is energized, the hydraulic oil of the second oil pump group returns to the oil tank through the second hydraulically controlled one-way valve and the second solenoid valve in sequence.

[0012] As a further improvement of the above scheme, the first reversing valve is a three-position six-way reversing valve, whose first oil port is connected to the oil port A of the test bench motor, and whose third oil port is connected to the oil port B of the test bench motor; whose fifth oil port and sixth oil port are respectively connected to the first oil pump group, and whose fourth oil port is connected to the back pressure oil return circuit; When the first reversing valve is in the first working position, its first oil port is connected to its sixth oil port, its third oil port is connected to its fourth oil port, and its second oil port and its fifth oil port are not connected to each other; When the first reversing valve is in the second working position (i.e., in the middle position), its second oil port is connected to its fifth oil port, and the other oil ports are not connected to each other; When the first reversing valve is in the third working position, its first oil port is connected with its fourth oil port, its third oil port is connected with its sixth oil port, and its second oil port and its fifth oil port are not connected with each other.

[0013] As a further improvement of the above scheme, the second reversing valve is a three-position six-way reversing valve, whose first oil port is connected to the B oil port of the tested motor, and whose third oil port is connected to the A oil port of the tested motor; whose fifth oil port and sixth oil port are respectively connected to the second oil pump group, and whose fourth oil port is connected to the oil tank; When the second reversing valve is in the first working position, its first oil port is connected to its sixth oil port, its third oil port is connected to its fourth oil port, and its second oil port and its fifth oil port are not connected to each other; When the second reversing valve is in the second working position (i.e., in the middle position), its second oil port is connected to its fifth oil port, and the other oil ports are not connected to each other; When the second reversing valve is in the third working position, its first oil port is connected with its fourth oil port, its third oil port is connected with its sixth oil port, and its second oil port and its fifth oil port are not connected with each other.

[0014] As a further improvement of the above solution, the first solenoid valve, the second solenoid valve and the third solenoid valve are all two-position four-way solenoid valves; In the first working position, the first oil port of each solenoid valve is connected to its fourth oil port, and the second oil port is connected to its third oil port; In the second working position, the first oil port of each solenoid valve is communicated with its third oil port, and the second oil port of each solenoid valve is communicated with its fourth oil port.

[0015] As a further improvement of the above scheme, the first oil port of the first solenoid valve is connected to the oil outlet of the first oil pump group, its second oil port is connected to the oil tank, and its third oil port is connected to the first hydraulically controlled one-way valve away from its conducting end.

[0016] As a further improvement of the above scheme, the first oil port of the second solenoid valve is connected to the oil outlet of the second oil pump group, its second oil port is connected to the oil tank, and its fourth oil port is connected to the second hydraulically controlled one-way valve away from its conducting end.

[0017] As a further improvement of the above scheme, the first oil port of the third solenoid valve is connected to the fourth oil port of the first reversing valve, its second oil port is connected to the oil tank, and its fourth oil port is connected to the third hydraulically controlled one-way valve away from its conducting end.

[0018] In a second aspect, the present invention further provides a control method for a hydraulic system of a power head motor reliability test, the steps of which include: S1. Alternating load simulation control method: S11, control the first reversing valve and the second reversing valve to be in the first working position, start the second oil pump group, drive the tested motor to rotate, and the tested motor drives the test bench motor to rotate; S12, alternately controlling the third solenoid valve to be powered on and off, so as to simulate the alternating load of the power head motor under severe working conditions; S2, the power head motor forward and reverse fast switching unloading simulation control method: S21, fast forward simulation Control the first reversing valve and the second reversing valve to be in the first working position, start the first oil pump group and the second oil pump group, the second oil pump group drives the tested motor to rotate in the forward direction, the tested motor drives the test bench motor to rotate, and the first oil pump group replenishes oil for the test bench motor; The third solenoid valve is controlled to lose power, and the test bench motor returns oil under the set back pressure torque of the second relief valve to simulate the fast forward rotation operation of the power head motor; S22, forward emergency stop simulation The second reversing valve is controlled to switch to the second working position, and the second oil pump group stops running to simulate the emergency stop of the power head motor. At the same time, the third solenoid valve is controlled to be energized, and the low-pressure oil of the test bench motor returns to the oil tank through its B oil port; The first reversing valve is in the first working position, and the first solenoid valve is controlled to be energized, the first hydraulically controlled one-way valve is closed, and the first oil pump group pumps high-pressure oil to the motor A of the test bench through the oil port thereof under the set pressure of the first relief valve, so as to drive the tested motor to rotate in the original direction to simulate the impact of the accumulated weight; S23, fast reversal simulation The first reversing valve and the second reversing valve are controlled to switch to the third working position, and the second oil pump group is turned on. The second oil pump group drives the tested motor to rotate in the reverse direction. At the same time, the third solenoid valve is controlled to lose power, and the back pressure loading port of the test bench motor overcomes the set overflow pressure of the third overflow valve and returns to the oil tank; At the same time, the first solenoid valve is controlled to lose power, and the first hydraulically controlled one-way valve is opened under low-pressure oil to simulate the rapid reversal operation of the power head motor; S24, repeat the steps S21, S22 and S23 to simulate the forward and reverse rotation of the power head motor to quickly switch to unload soil.

[0019] As a further improvement of the above solution, in step S12, when the third solenoid valve is alternately controlled to be powered on and off, S121, controlling the third solenoid valve to lose power, and the test bench motor returns oil under the set back pressure torque of the second relief valve to simulate the working condition of the power head motor under high load; S122, controlling the third solenoid valve to be energized, so that the low-pressure oil of the test bench motor flows into and conducts the third hydraulically controlled one-way valve, and then returns the oil through the third solenoid valve to simulate the operating condition of the power head motor under low load.

[0020] As a further improvement of the above solution, in step S1, the first oil pump group is started at the same time to replenish oil for the test bench motor in time to prevent air suction.

[0021] Since the present invention adopts the above technical solution, the beneficial effects of this application are: The present invention provides a hydraulic system for reliability testing of a power head motor, which is provided with two oil pump groups, respectively used to drive a test bench motor and a motor to be tested, and at the same time, the motor to be tested and the motor to be tested are arranged to drive each other. When the second oil pump group is started, the motor to be tested drives the test bench motor to rotate. At the same time, a third overflow valve, a third hydraulically controlled one-way valve and a third solenoid valve are arranged on the back-pressure return oil circuit of the test bench motor, which are used to control and adjust the back-pressure torque of the test bench motor. Specifically, the third overflow valve and the third hydraulically controlled one-way valve are arranged in parallel, and the third solenoid valve is connected to the far-from-conducting end of the third hydraulically controlled one-way valve. When the third solenoid valve loses power, the test bench The motor back pressure torque is set by the third relief valve, and the set pressure of the third relief valve is controlled and adjusted to simulate the working condition of the power head motor under high load; when the third solenoid valve is energized, the test bench motor is unloaded through the third hydraulically controlled one-way valve and the third solenoid valve in sequence to simulate the working condition of the power head motor under low load; such a setting is convenient for changing the return oil back pressure and back pressure torque of the test bench motor by alternatingly controlling the on and off of the third solenoid valve, thereby realizing the alternating change of the operating load of the tested motor from highest-lowest-highest-lowest, and then realizing the alternating load condition of the power head motor of the simulated rotary drilling rig in the construction of harsh bottom layers such as broken rock and pebble layers; In addition, a first reversing valve is arranged between the first oil pump group and the test bench motor, and a second reversing valve is arranged between the second oil pump group and the motor to be tested, and both reversing valves have a mid-position function; the setting of the two reversing valves can simulate the forward and reverse rapid switching of the power head motor to unload soil by controlling the switching of the first reversing valve and the second reversing valve to the corresponding working positions; with such a setting, the test hydraulic system provided by the present invention can effectively simulate the rotary drilling rig in harsh working conditions, so that the reliability of the new power head motor can be tested through the test bench motor, greatly shortening the application verification time of the power head motor. BRIEF DESCRIPTION OF THE DRAWINGS

[0022] In order to more clearly illustrate the embodiments of the present invention or the technical solutions in the prior art, the drawings required for use in the embodiments or the description of the prior art will be briefly introduced below. Obviously, the drawings described below are only some embodiments of the present invention. For ordinary technicians in this field, other drawings can be obtained based on the structures shown in these drawings without paying any creative work.

[0023] Figure 1 A schematic diagram of a hydraulic system for reliability testing of a power head motor disclosed in the present invention (motor driven forward rotation) Figure 1 ; Figure 2 A schematic diagram of a hydraulic system (motor emergency stop) for reliability testing of a power head motor disclosed in the present invention Figure 2 ; Figure 3 A schematic diagram of a hydraulic system for reliability testing of a power head motor (motor drive reverse) disclosed in the present invention Figure 3 ; Figure 4 It is a cross-sectional schematic diagram of a drilling operation of a power head motor driving a power transmission drill rod and a drilling tool for breaking a rock layer or a pebble layer disclosed in the present invention; Figure 5 It is a top view schematic diagram of the power head motor driving the power transmission drill rod drilling tool disclosed in the present invention to break rock or pebble layers for drilling operation; Figure 6 The schematic diagram of the rotary drilling power head disclosed in the present invention is a forward and reverse switching operation for unloading soil, wherein Figure 6 (a) is the schematic diagram of the power head rotating forward. Figure 6 (b) is a schematic diagram of the emergency stop operation of the power head. Figure 6 (c) is a schematic diagram of the power head reversal operation.

[0024] Reference numerals: 1. First oil pump group; 2. Second oil pump group; 3. First reversing valve; 4. Test bench motor; 5. Tested motor; 6. Second reversing valve; 7a, first overflow valve; 7b, second overflow valve; 7c, third overflow valve; 8a, first hydraulically controlled one-way valve; 8b, second hydraulically controlled one-way valve; 8c, third hydraulically controlled one-way valve; 9a, first solenoid valve; 9b, second solenoid valve; 9c, third solenoid valve; 01. Drill rod for transmitting force; 02. Drilling tools; 03. Drill teeth; 04. Crushing rocks or pebbles.

[0025] The realization of the purpose, functional features and advantages of the present invention will be further explained in conjunction with the implementation methods and with reference to the accompanying drawings. DETAILED DESCRIPTION

[0026] The following will be combined with the drawings in the embodiments of the present invention to clearly and completely describe the technical solutions in the embodiments of the present invention. Obviously, the described embodiments are only part of the embodiments of the present invention, not all of the embodiments. Based on the embodiments of the present invention, all other embodiments obtained by ordinary technicians in this field without creative work are within the scope of protection of the present invention.

[0027] It should be noted that all directional indications (such as up, down, etc.) in the embodiments of the present invention are only used to explain the relative position relationship, movement status, etc. between the components under a certain specific posture (as shown in the accompanying drawings). If the specific posture changes, the directional indication will also change accordingly.

[0028] In addition, in the present invention, the descriptions of "first", "second", etc. are only used for descriptive purposes and cannot be understood as indicating or implying their relative importance or implicitly indicating the number of the indicated technical features. Therefore, the features defined as "first" or "second" may explicitly or implicitly include at least one of the features.

[0029] Furthermore, the technical solutions between the various embodiments of the present invention may be combined with each other, but this must be based on the fact that they can be implemented by ordinary technicians in the field. When the combination of technical solutions is mutually contradictory or cannot be implemented, it should be deemed that such combination of technical solutions does not exist and is not within the scope of protection required by the present invention.

[0030] Example 1 In order to illustrate the inventive concept of the present invention, in this embodiment, a rotary drilling rig power head motor is taken as an example for explanation. When the rotary drilling rig power head motor is in operation, Figure 4 and Figure 5, the power head motor needs to drive the force transmission drill rod 01 and the drill tool 02 in sequence, and finally transmit it to the drill teeth 03 to break the rock or pebble 04. Due to the incompleteness and discontinuity of the broken rock or pebble 04, the resistance of the drill tool 02 is an alternating change of maximum-minimum-maximum-minimum. This alternating resistance change will affect the alternating change of the working load of the driving element-the power head motor. Therefore, the power head motor reliability test hydraulic system provided by the present invention must first solve the problem of being able to simulate the alternating load suddenly encountered during the drilling operation of breaking rock or pebble layers; In addition, during the operation of the rotary drilling rig power head motor, the forward and reverse rotations must be quickly switched to discharge the soil. During this process, the power head motor needs to withstand the alternating impact of large inertia. For details, see Figure 6 The process of the power head quickly switching to unload soil can be decomposed into a cyclic switching of fast forward rotation → forward rotation emergency stop → switching to reverse rotation; therefore, the hydraulic system for reliability testing of the power head motor provided by the present invention is also capable of simulating the cyclic switching of fast forward rotation, forward rotation emergency stop and switching to reverse rotation, so as to simulate the alternating impact of large inertia that the power head motor needs to withstand when the forward and reverse rotations are quickly switched to unload soil; Based on the above invention motivation, the present invention provides a hydraulic system for testing the reliability of a power head motor. Figure 1-Figure 3 , comprising a first oil pump group 1 and a second oil pump group 2, wherein the first oil pump group 1 is connected to a test bench motor 4 via a first reversing valve 3, the second oil pump group 2 is used to be connected to a motor under test 5, and a second reversing valve 6 is further provided between the second oil pump group 2 and the motor under test 5; the test bench motor 4 and the motor under test 5 are driven and connected to each other; A first overflow valve 7a, a first hydraulically controlled one-way valve 8a and a first solenoid valve 9a are provided between the first oil pump group 1 and the first reversing valve 3, and are used to control and adjust the operating pressure of the first oil pump group 1; The first overflow valve 7a and the first hydraulically controlled one-way valve 8a are arranged in parallel, and the first solenoid valve 9a is connected to the end of the first hydraulically controlled one-way valve 8a away from the conduction end; When the first solenoid valve 9a is energized, the first hydraulically controlled one-way valve 8a is closed through the first solenoid valve 9a, and the operating pressure of the first oil pump group 1 is set by the first overflow valve 7a; when the first solenoid valve 9a is de-energized, the hydraulic oil of the first oil pump group 1 returns to the oil tank through the first hydraulically controlled one-way valve 8a and the first solenoid valve 9a in sequence; A second overflow valve 7b, a second hydraulically controlled one-way valve 8b and a second solenoid valve 9b are provided between the second oil pump group 2 and the second reversing valve 6, for controlling and adjusting the operating pressure of the second oil pump group 2; The second overflow valve 7b and the second hydraulically controlled one-way valve 8b are arranged in parallel, and the second solenoid valve 9b is connected to the end away from the conduction end of the second hydraulically controlled one-way valve 8b; When the second solenoid valve 9b loses power, the second hydraulically controlled one-way valve 8b is closed through the second solenoid valve 9b, and the operating pressure of the second oil pump group 2 is set by the second overflow valve 7b; when the second solenoid valve 9b is energized, the hydraulic oil of the second oil pump group 2 returns to the oil tank through the second hydraulically controlled one-way valve 8b and the second solenoid valve 9b in sequence.

[0031] The back pressure oil return line of the test bench motor 4 is provided with a third overflow valve 7c, a third hydraulically controlled one-way valve 8c and a third solenoid valve 9c, which are used to control and adjust the back pressure torque of the test bench motor 4; The third relief valve 7c and the third hydraulically controlled one-way valve 8c are arranged in parallel, and the third solenoid valve 9c is connected to the end away from the conduction end of the third hydraulically controlled one-way valve 8c. When the third solenoid valve 9c loses power, the back pressure torque of the test bench motor 4 is set by the third relief valve 7c; when the third solenoid valve 9c is energized, the test bench motor 4 is unloaded by the third hydraulically controlled one-way valve 8c and the third solenoid valve 9c in sequence; the first reversing valve 3 and the second reversing valve 6 are both reversing valves with a neutral position function; In the present invention, two oil pump groups are provided, which are respectively used to drive the test bench motor 4 and the tested motor 5. At the same time, the tested motor 5 and the test bench motor 4 are arranged to drive each other. When the second oil pump group 2 is started, the tested motor 5 drives the test bench motor 4 to rotate. At the same time, a third overflow valve 7c, a third hydraulically controlled one-way valve 8c and a third solenoid valve 9c are provided on the back pressure return oil line of the test bench motor 4 to control and adjust the back pressure torque of the test bench motor 4. Specifically, the third overflow valve 7c and the third hydraulically controlled one-way valve 8c are arranged in parallel, and the third solenoid valve 9c is connected to the far-from-conduction end of the third hydraulically controlled one-way valve 8c. When the third solenoid valve 9c loses power, the back pressure return oil line of the test bench motor 4 The pressure torque is set by the third relief valve 7c, and the set pressure of the third relief valve 7c is controlled and adjusted to simulate the working condition of the power head motor under high load; when the third solenoid valve 9c is energized, the test bench motor 4 is unloaded through the third hydraulically controlled one-way valve 8c and the third solenoid valve 9c in sequence to simulate the working condition of the power head motor under low load; such a setting is convenient for changing the return oil back pressure and back pressure torque of the test bench motor 4 by alternatingly controlling the on and off of the third solenoid valve 9c, thereby realizing the alternating operation load of the tested motor 5 from the highest-lowest-highest-lowest, and then realizing the alternating load condition of the power head motor of the simulated rotary drilling rig in the construction of harsh bottom layers such as broken rock and pebble layers; In addition, a first reversing valve 3 is arranged between the first oil pump group 1 and the test bench motor 4, and a second reversing valve 6 is arranged between the second oil pump group 2 and the tested motor 5, and both reversing valves have a mid-position function; the setting of the two reversing valves can simulate the forward and reverse rapid switching of the power head motor to unload soil by controlling the switching of the first reversing valve 3 and the second reversing valve 6 to the corresponding working positions; with such a setting, the test hydraulic system provided by the present invention can effectively simulate the rotary drilling rig in harsh working conditions, so that the reliability of the new power head motor can be tested through the test bench motor 4, greatly shortening the application verification time of the power head motor.

[0032] As a preferred embodiment, the first reversing valve 3 is a three-position six-way reversing valve, the first oil port of which is connected to the oil port A of the test bench motor 4, and the third oil port of which is connected to the oil port B of the test bench motor 4; the fifth oil port and the sixth oil port of which are respectively connected to the first oil pump group 1, and the fourth oil port of which is connected to the back pressure oil return oil circuit; When the first reversing valve 3 is in the first working position, its first oil port is connected to its sixth oil port, its third oil port is connected to its fourth oil port, and its second oil port and its fifth oil port are not connected to each other; When the first reversing valve 3 is in the second working position (i.e., in the middle position), its second oil port is connected to its fifth oil port, and the other oil ports are not connected to each other; When the first reversing valve 3 is in the third working position, its first oil port is connected to its fourth oil port, its third oil port is connected to its sixth oil port, and its second oil port is not connected to its fifth oil port; The second reversing valve 6 is a three-position six-way reversing valve, the first oil port of which is connected to the oil port B of the tested motor 5, and the third oil port of which is connected to the oil port A of the tested motor 5; the fifth oil port and the sixth oil port of which are respectively connected to the second oil pump group 2, and the fourth oil port of which is connected to the oil tank; When the second reversing valve 6 is in the first working position, its first oil port is connected to its sixth oil port, its third oil port is connected to its fourth oil port, and its second oil port and its fifth oil port are not connected to each other; When the second reversing valve 6 is in the second working position (i.e., in the middle position), its second oil port is connected to its fifth oil port, and the other oil ports are not connected to each other; When the second reversing valve 6 is in the third working position, its first oil port is connected to its fourth oil port, its third oil port is connected to its sixth oil port, and its second oil port is not connected to its fifth oil port; With such an arrangement, when the second oil pump group 2 drives the tested motor 5 to rotate in the forward direction, the first reversing valve 3 and the second reversing valve 6 are first switched to the first working position. At this time, the oil outlet of the second oil pump group 2 is connected with the sixth oil port of the second reversing valve 6, and the high-pressure oil enters the second reversing valve 6 through its sixth oil port and then flows out through its first oil port, and then enters the B oil port of the tested motor 5 to drive the tested motor 5 to rotate in the forward direction, and the low-pressure oil enters the third oil port of the second reversing valve 6 through its A oil port and then returns to the oil tank through its fourth oil port; at the same time, the tested motor 5 drives the test bench motor 4 to rotate. At the same time, in order to prevent the test bench motor 4 from being sucked into the air, the oil outlet of the first pump group is connected with the sixth oil port of the first reversing valve 3. The hydraulic oil enters the first reversing valve 3 through its sixth oil port and then flows out through its first oil port, and then enters the A oil port of the test bench motor 4 to replenish the oil of the test bench motor 4; the hydraulic oil then flows out through the B oil port of the test bench motor 4 and enters the third oil port of the first reversing valve 3, and then passes through its fourth oil port and returns to the oil tank through the third overflow valve 7c or returns to the oil tank through the third hydraulically controlled one-way and the third solenoid valve 9c; By analogy, by switching the first reversing valve 3 and the second reversing valve 6 to the corresponding working positions and controlling the on and off of the third solenoid valve 9c, different operating conditions of the power head motor can be simulated, thereby achieving reliability testing of the power head motor.

[0033] As a preferred embodiment, the first solenoid valve 9a, the second solenoid valve 9b and the third solenoid valve 9c are all two-position four-way solenoid valves; In the first working position, the first oil port of each solenoid valve is connected to its fourth oil port, and the second oil port is connected to its third oil port; In the second working position, the first oil port of each solenoid valve is connected to its third oil port, and the second oil port is connected to its fourth oil port; The first oil port of the first solenoid valve 9a is connected to the oil outlet of the first oil pump group 1, the second oil port is connected to the oil tank, and the third oil port is connected to the end of the first hydraulically controlled one-way valve 8a away from the conducting end; The first oil port of the second solenoid valve 9b is connected to the oil outlet of the second oil pump group 2, the second oil port is connected to the oil tank, and the fourth oil port is connected to the end of the second hydraulically controlled one-way valve 8b away from the conducting end; The first oil port of the third solenoid valve 9c is connected to the fourth oil port of the first reversing valve 3, the second oil port is connected to the oil tank, and the fourth oil port is connected to the end of the third hydraulically controlled one-way valve 8c away from the conducting end; The setting of three two-position four-way solenoid valves can realize the closing and opening of the corresponding hydraulically controlled one-way valve by switching the solenoid valve to the corresponding working position; the setting of the hydraulically controlled one-way valve and the relief valve at the first oil pump group 1 and the second oil pump group 2 can increase the stable system pressure for the corresponding motor and ensure the smooth and effective test. At the same time, the setting of the relief valve provides safety protection for this hydraulic system; The third hydraulically controlled one-way valve 8c and the third overflow valve 7c are arranged to simulate the alternating load of the power head motor by alternately controlling the third solenoid valve 9c.

[0034] Example 2 The present invention also provides a control method for a hydraulic system for reliability testing of a power head motor as provided in Example 1, the steps of which include: S1. Alternating load simulation control method: S11, control the first reversing valve 3 and the second reversing valve 6 to be in the first working position, start the second oil pump group 2, drive the tested motor 5 to rotate, and the tested motor 5 drives the test bench motor 4 to rotate; S12, alternately controlling the third solenoid valve 9c to be powered on and off, so as to simulate the alternating load of the power head motor under severe working conditions; Specifically, when the third solenoid valve 9c is alternately controlled to be powered on and off, S121, controlling the third solenoid valve 9c to lose power, and the test bench motor 4 returns oil under the set back pressure torque of the second relief valve 7b to simulate the working condition of the power head motor under high load; S122, controlling the third solenoid valve 9c to be energized, so that the low-pressure oil of the test bench motor 4 flows into and conducts the third hydraulically controlled one-way valve 8c, and then returns the oil through the third solenoid valve 9c, so as to simulate the working condition of the power head motor under low load; S2, the power head motor forward and reverse fast switching unloading simulation control method: S21, fast forward simulation The first reversing valve 3 and the second reversing valve 6 are both controlled to be in the first working position, and the first oil pump group 1 and the second oil pump group 2 are turned on. The second oil pump group 2 drives the tested motor 5 to rotate in the forward direction, and the tested motor 5 drives the test bench motor 4 to rotate. The first oil pump group 1 replenishes oil for the test bench motor 4; The third solenoid valve 9c is controlled to lose power, and the test bench motor 4 returns oil under the set back pressure torque of the second relief valve 7b to simulate the fast forward rotation operation of the power head motor; By alternately controlling the on and off of the third solenoid valve 9c, the oil return back pressure and back pressure torque of the test bench motor 4 are alternately changed, so that the operating load of the tested motor 5 is alternately changed from the highest-lowest-highest-lowest, and the alternating load working condition of the power head motor of the rotary drilling rig in the harsh bottom layer such as broken rock and pebble layer is simulated; S22, forward emergency stop simulation The second reversing valve 6 is controlled to switch to the second working position (i.e., the middle position), and the second oil pump group 2 stops running to simulate the emergency stop of the power head motor. At the same time, the third solenoid valve 9c is controlled to be energized, and the low-pressure oil of the test bench motor 4 returns to the oil tank through its B oil port; The first reversing valve 3 is in the first working position, and at the same time controls the first solenoid valve 9a to be energized, the first hydraulically controlled one-way valve 8a is closed, and the first oil pump group 1 pumps high-pressure oil to the test bench motor 4A through the oil port thereof under the set pressure of the first relief valve 7a, so as to drive the tested motor 5 to rotate in the original direction to simulate the impact of accumulated heavy objects such as drill pipes, drilling tools 02, and slag; S23, fast reversal simulation The first reversing valve 3 and the second reversing valve 6 are controlled to switch to the third working position, the second oil pump group 2 is turned on, the second oil pump group 2 drives the tested motor 5 to rotate in the reverse direction, and the third solenoid valve 9c is controlled to lose power at the same time, so that the back pressure loading port of the test bench motor 4 overcomes the set overflow pressure of the third overflow valve 7c and returns to the oil tank; At the same time, the first solenoid valve 9a is controlled to lose power, and the first hydraulically controlled one-way valve 8a is opened under low-pressure oil to simulate the rapid reversal operation of the power head motor; S24, repeating steps S21, S22 and S23 to simulate the forward and reverse rotation of the power head motor to quickly switch to unload soil; Such a setting can effectively simulate the complex working conditions of the power head motor suddenly encountering alternating loads when drilling in broken rock or pebble layers, and can also effectively simulate the working conditions where the power head motor is subjected to alternating impacts during rapid switching of forward and reverse rotations to discharge soil.

[0035] As a preferred embodiment, in step S1, the first oil pump group 1 is turned on at the same time to replenish oil to the test bench motor 4 in time to prevent air suction.

[0036] The above are only preferred embodiments of the present invention, and are not intended to limit the patent scope of the present invention. All equivalent structural changes made using the contents of the present invention's specification and drawings, or directly / indirectly applied in other related technical fields, are included in the patent protection scope of the present invention.

Claims

1. A hydraulic system for reliability testing of a power head motor, characterized in that: The invention comprises a first oil pump group, a second oil pump group and a test bench motor, wherein the first oil pump group is connected to the test bench motor through a first reversing valve, the second oil pump group is used to be connected to a motor under test, and a second reversing valve is further provided between the second oil pump group and the motor under test; the test bench motor and the motor under test are mutually drivingly connected; A third relief valve, a third hydraulically controlled one-way valve and a third solenoid valve are provided on the back pressure return oil line of the test bench motor, which are used to control and adjust the back pressure torque of the test bench motor; The third relief valve and the third hydraulically controlled one-way valve are arranged in parallel, and the third solenoid valve is connected to the end away from the conduction end of the third hydraulically controlled one-way valve. When the third solenoid valve loses power, the back pressure torque of the test bench motor is set by the third relief valve; when the third solenoid valve is energized, the test bench motor is unloaded through the third hydraulically controlled one-way valve and the third solenoid valve in sequence; The first reversing valve and the second reversing valve are both reversing valves with a mid-position function.

2. A hydraulic system for reliability testing of a power head motor according to claim 1, characterized in that: A first relief valve, a first hydraulically controlled one-way valve and a first solenoid valve are provided between the first oil pump group and the first reversing valve, for controlling and adjusting the operating pressure of the first oil pump group; The first relief valve and the first hydraulically controlled one-way valve are arranged in parallel, and the first solenoid valve is connected to the end away from the conduction end of the first hydraulically controlled one-way valve; When the first solenoid valve is energized, the first hydraulically controlled one-way valve is closed through the first solenoid valve, and the operating pressure of the first oil pump group is set through the first relief valve; When the first solenoid valve loses power, the hydraulic oil of the first oil pump group returns to the oil tank through the first hydraulically controlled one-way valve and the first solenoid valve in sequence.

3. A hydraulic system for reliability testing of a power head motor according to claim 2, characterized in that: A second relief valve, a second hydraulically controlled one-way valve and a second solenoid valve are provided between the second oil pump group and the second reversing valve, for controlling and adjusting the operating pressure of the second oil pump group; The second overflow valve and the second hydraulically controlled one-way valve are arranged in parallel, and the second solenoid valve is connected to the end away from the conduction end of the second hydraulically controlled one-way valve; When the second solenoid valve loses power, the second hydraulically controlled one-way valve is closed by the second solenoid valve, and the operating pressure of the second oil pump group is set by the second relief valve; When the second solenoid valve is energized, the hydraulic oil of the second oil pump group returns to the oil tank through the second hydraulically controlled one-way valve and the second solenoid valve in sequence.

4. A hydraulic system for reliability testing of a power head motor according to any one of claims 1 to 3, characterized in that: The first reversing valve is a three-position six-way reversing valve, whose first oil port is connected to the oil port A of the test bench motor, and whose third oil port is connected to the oil port B of the test bench motor; whose fifth oil port and sixth oil port are respectively connected to the first oil pump group, and whose fourth oil port is connected to the back pressure oil return circuit; When the first reversing valve is in the first working position, its first oil port is connected to its sixth oil port, its third oil port is connected to its fourth oil port, and its second oil port and its fifth oil port are not connected to each other; When the first reversing valve is in the second working position, its second oil port and its fifth oil port are connected, and the other oil ports are not connected to each other; When the first reversing valve is in the third working position, its first oil port is connected with its fourth oil port, its third oil port is connected with its sixth oil port, and its second oil port and its fifth oil port are not connected with each other.

5. A hydraulic system for reliability testing of a power head motor according to any one of claims 1 to 3, characterized in that: The second reversing valve is a three-position six-way reversing valve, whose first oil port is connected to the oil port B of the tested motor, and whose third oil port is connected to the oil port A of the tested motor; whose fifth oil port and sixth oil port are respectively connected to the second oil pump group, and whose fourth oil port is connected to the oil tank; When the second reversing valve is in the first working position, its first oil port is connected to its sixth oil port, its third oil port is connected to its fourth oil port, and its second oil port and its fifth oil port are not connected to each other; When the second reversing valve is in the second working position, its second oil port and its fifth oil port are connected, and the other oil ports are not connected to each other; When the second reversing valve is in the third working position, its first oil port is connected with its fourth oil port, its third oil port is connected with its sixth oil port, and its second oil port and its fifth oil port are not connected with each other.

6. A hydraulic system for reliability testing of a power head motor according to claim 3, characterized in that: The first solenoid valve, the second solenoid valve and the third solenoid valve are all two-position four-way solenoid valves; In the first working position, the first oil port of each solenoid valve is connected to its fourth oil port, and the second oil port is connected to its third oil port; In the second working position, the first oil port of each solenoid valve is communicated with its third oil port, and the second oil port of each solenoid valve is communicated with its fourth oil port.

7. A hydraulic system for reliability testing of a power head motor according to claim 6, characterized in that: The first oil port of the first solenoid valve is connected to the oil outlet of the first oil pump group, the second oil port is connected to the oil tank, and the third oil port is connected to the end of the first hydraulically controlled one-way valve away from the conducting end; The first oil port of the second solenoid valve is connected to the oil outlet of the second oil pump group, the second oil port is connected to the oil tank, and the fourth oil port is connected to the end of the second hydraulically controlled one-way valve away from the conducting end; The first oil port of the third solenoid valve is connected to the fourth oil port of the first reversing valve, the second oil port is connected to the oil tank, and the fourth oil port is connected to the third hydraulically controlled one-way valve away from the conducting end.

8. A control method for a hydraulic system for reliability testing of a power head motor, comprising a hydraulic system for reliability testing of a power head motor as claimed in any one of claims 1 to 7, characterized in that: The steps of the control method include: S1. Alternating load simulation control method: S11, control the first reversing valve and the second reversing valve to be in the first working position, start the second oil pump group, drive the tested motor to rotate, and the tested motor drives the test bench motor to rotate; S12, alternately controlling the third solenoid valve to be powered on and off, so as to simulate the alternating load of the power head motor under severe working conditions; S2, the power head motor forward and reverse fast switching unloading simulation control method: S21, fast forward simulation Control the first reversing valve and the second reversing valve to be in the first working position, start the first oil pump group and the second oil pump group, the second oil pump group drives the tested motor to rotate in the forward direction, the tested motor drives the test bench motor to rotate, and the first oil pump group replenishes oil for the test bench motor; The third solenoid valve is controlled to lose power, and the test bench motor returns oil under the set back pressure torque of the second relief valve to simulate the fast forward rotation operation of the power head motor; S22, forward emergency stop simulation The second reversing valve is controlled to switch to the second working position, and the second oil pump group stops running to simulate the emergency stop of the power head motor. At the same time, the third solenoid valve is controlled to be energized, and the low-pressure oil of the test bench motor returns to the oil tank through its B oil port; The first reversing valve is in the first working position, and the first solenoid valve is controlled to be energized, the first hydraulically controlled one-way valve is closed, and the first oil pump group pumps high-pressure oil to the motor A of the test bench through the oil port thereof under the set pressure of the first relief valve, so as to drive the tested motor to rotate in the original direction to simulate the impact of the accumulated weight; S23, fast reversal simulation The first reversing valve and the second reversing valve are controlled to switch to the third working position, and the second oil pump group is turned on. The second oil pump group drives the tested motor to rotate in the reverse direction. At the same time, the third solenoid valve is controlled to lose power, and the back pressure loading port of the test bench motor overcomes the set overflow pressure of the third overflow valve and returns to the oil tank; At the same time, the first solenoid valve is controlled to lose power, and the first hydraulically controlled one-way valve is opened under low-pressure oil to simulate the rapid reversal operation of the power head motor; S24, repeat the steps S21, S22 and S23 to simulate the forward and reverse rotation of the power head motor to quickly switch to unload soil.

9. The control method according to claim 8, characterized in that: In step S12, the third solenoid valve is alternately controlled to be powered on and off. S121, controlling the third solenoid valve to lose power, and the test bench motor returns oil under the set back pressure torque of the second relief valve to simulate the working condition of the power head motor under high load; S122, controlling the third solenoid valve to be energized, so that the low-pressure oil of the test bench motor flows into and conducts the third hydraulically controlled one-way valve, and then returns the oil through the third solenoid valve to simulate the operating condition of the power head motor under low load.

10. The control method according to claim 8 or 9, characterized in that: In step S1, the first oil pump group is started at the same time to replenish oil to the test bench motor in time to prevent air suction.

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