A test bench for operation of an air conditioner of a new energy vehicle

Abstract

The application discloses a kind of for new energy automobile air conditioner running test bench, it is related to automobile air conditioner test technical field, comprising: outer frame;Refrigerant circulation loop, fixed integrated in the outer frame, including sequentially closed loop connection according to refrigerant flow direction: condenser, mass flow meter, electronic expansion valve, evaporator and the pipeline that communicates each other;Controller is configured to monitor the operating parameter of the refrigerant circulation loop;Compressor adjustment component is set in the outer frame, including: pedestal, fixed in the outer frame;Two symmetrically arranged rotating shafts are rotatably supported on the pedestal, and the axis of the rotating shaft extends along the horizontal direction;Positioning assembly is arranged between the two rotating shafts, configured to position the measured compressor between the two rotating shafts, and make the measured compressor access the refrigerant circulation loop;Angle adjustment component is configured to drive the rotating shaft to rotate to realize relevant test.

Description

Technical Field

[0001] This invention relates to the field of automotive air conditioning testing technology, and more specifically to a test bench for the operation of air conditioning systems in new energy vehicles. Background Technology

[0002] The air conditioning compressors in new energy vehicles (especially pure electric vehicles) are directly driven by high-voltage DC motors. They have a wide operating speed range, and the compressor relies on refrigerant oil to lubricate and cool moving parts such as the scroll plate, bearings, and main shaft. The refrigerant oil is stored at the bottom of the compressor housing and is delivered to various lubrication points through the centrifugal pump effect generated when the main shaft rotates via an eccentric oil passage at the lower end of the main shaft.

[0003] Vehicles experience various posture changes during actual road driving, including uphill and downhill driving, sharp turns, and road bumps. When a vehicle is in a tilted posture for an extended period (e.g., continuously uphill) or frequently experiences road bumps, the refrigerant oil level inside the compressor housing tilts or violently fluctuates with the posture changes. This can cause the oil inlet area at the lower end of the main shaft to be exposed above the oil surface, resulting in oil shortage. Once oil shortage occurs, the lubrication and cooling of the moving parts inside the compressor will rapidly deteriorate, manifesting as a sharp increase in exhaust temperature, increased fluctuations in motor input current, and abnormally increased vibration amplitude of the housing.

[0004] Existing test benches for air conditioning compressors in new energy vehicles primarily focus on the compressor's cooling performance parameters (cooling capacity, COP, power consumption, etc.), typically conducting steady-state or transient performance tests with the compressor held horizontally and stationary. These benches cannot simulate the dynamic changes in the compressor's internal oil circuit caused by inclines or bumps during actual vehicle operation, and therefore cannot evaluate the compressor's resistance to oil shortage under tilted and bumpy conditions.

[0005] Furthermore, different models of electric compressors have different housing dimensions, internal oil sump geometry, and the height of the main shaft oil inlet area relative to the mounting base. If a tilt test is conducted using a uniform installation method (e.g., using the mounting base of all compressors as the rotation reference), the distance between the main shaft oil inlet area and the rotation axis will be different for different compressors. This results in inconsistent exposure of the oil inlet area for different compressors at the same tilt angle, making the test results lack lateral comparability.

[0006] Therefore, it is necessary to provide a test bench for the operation of air conditioning in new energy vehicles to solve the above problems. Summary of the Invention

[0007] To address the above problems, the present invention provides the following technical solution: a test bench for the operation of air conditioning in new energy vehicles, comprising: outer frame; The refrigerant circulation loop is fixedly integrated within the outer frame and includes, in a closed loop connected sequentially in the refrigerant flow direction, a condenser, a mass flow meter, an electronic expansion valve, an evaporator, and pipelines connecting the above components. The controller is configured to monitor the operating parameters of the refrigerant circulation loop; A compressor regulating assembly, disposed within the outer frame, includes: The base is fixed within the outer frame; Two symmetrically arranged rotating shafts are rotatably supported on the base, and the axes of the rotating shafts extend in the horizontal direction; A positioning component, disposed between the two rotating shafts, is configured to position the compressor under test between the two rotating shafts and to connect the compressor under test to the refrigerant circulation loop; An angle adjustment component is configured to drive one of the shafts to rotate, thereby causing the compressor under test to reciprocate or tilt to a target angle and maintain it about the axis of the shaft.

[0008] Furthermore, preferably, the compressor adjustment assembly also includes a carrier plate located below the positioning assembly and connected to the positioning assembly via an elastic load assembly; The carrier plate is configured to support the compressor under test and can adjust the height of the compressor under test in the vertical direction so that the internal oil suction port of the compressor under test corresponds to the axis of the rotating shaft in the height position, and then the positioning component locks and positions the compressor under test.

[0009] Further, preferably, the angle adjustment component includes: A rotating drum is rotatably mounted on the base and driven by a first motor. A limit groove is formed on the peripheral wall of the rotating drum. A swing arm, one end of which is fixedly connected to the corresponding rotating shaft, and the other end of which is rotatably connected to a rotating wheel; The rotating wheel is constrained within the limiting groove, and the extension trajectory of the limiting groove is configured such that when the rotating drum rotates continuously in one direction, the rotating wheel moves cyclically along the limiting groove and drives the swing arm to swing back and forth around the axis of the rotating shaft, so as to simulate the dynamic disturbance of road bumps to the internal oil circuit of the compressor when the vehicle is driving.

[0010] Furthermore, as a preferred embodiment, the extension trajectory of the limiting groove is configured such that the maximum angle at which the swing arm swings from the horizontal position to one side is 5° to 25°. The first motor is configured to have a reciprocating oscillation mode and a precise angle mode: In the reciprocating swing mode, the first motor drives the rotating drum to rotate continuously, and the swing arm swings back and forth between 0° and the maximum angle; In the precise angle mode, the first motor drives the drum to rotate to a specified angle and locks it, so that the compressor under test is kept at the corresponding tilt angle.

[0011] Further, preferably, the positioning component includes: The mounting frame has a through slot running vertically through its middle section, through which the compressor under test passes. The second motor is fixed to one side of the mounting frame. The second motor has a first drive end and a second drive end. The first drive end is coaxially fixed with a first gear. The first rack slides through one side of the mounting frame and meshes with the first gear; The first clamping plate is fixed to the end of the first rack away from the first gear; The first guide seat is fixed to the mounting frame and provides sliding guidance for the first clamping plate through the first guide rod.

[0012] Furthermore, preferably, a second gear is coaxially fixed to the second drive end, the second gear meshes with a second rack, and a second clamping plate is fixed to the end of the second rack away from the second gear; a second guide seat is fixed to the opposite side of the mounting frame, and the second guide seat provides sliding guidance for the second clamping plate through a second guide rod.

[0013] Furthermore, as a preferred embodiment, both the first clamping plate and the second clamping plate have multiple holes, and each hole has a pressing post that slides through it. A pre-tensioning spring is connected between the pressing post and the hole. When the first clamping plate and the second clamping plate clamp the compressor under test, each pressing post elastically presses against the outer surface of the compressor under test under the action of the pre-tensioning spring.

[0014] Further, preferably, the resilient load-bearing component includes: A bottom connecting seat and a top connecting seat, wherein the top connecting seat has a notch in the middle; Multiple limiting rods are connected between the bottom connecting seat and the top connecting seat; A slide block passes through the notch and is slidably connected to each of the limiting rods; At least one spring is connected between the bottom connecting seat and the slide.

[0015] Furthermore, preferably, an exhaust pressure sensor and an exhaust temperature sensor are provided on the pipeline between the exhaust port of the compressor under test and the condenser; and an intake pressure sensor and an intake temperature sensor are provided on the pipeline between the refrigerant side outlet of the evaporator and the intake port of the compressor under test.

[0016] Compared with the prior art, the present invention provides a test bench for the operation of air conditioning in new energy vehicles, which has the following advantages: In this invention, the angle adjustment component can realize two motion modes: reciprocating swing and precise angle positioning. The former is used to simulate the dynamic disturbance of the oil surface caused by road bumps, while the latter is used to determine the critical tilt angle after the oil shortage is exposed. There is no need to transfer the compressor under test between two sets of equipment, resulting in high testing efficiency and good consistency.

[0017] In this invention, the vertical height of the compressor under test is adjusted by a carrier plate, and its height position is locked by a compressor adjustment component, so that its internal oil suction port corresponds to the axis of the rotating shaft. This ensures that the test conditions for different models of compressors are consistent, and the test results directly reflect the anti-tilting capability of the oil sump design itself, eliminating the interference of installation geometric differences.

[0018] In this invention, the entire refrigerant circulation loop, except for the compressor under test, is fixed inside the outer frame. The compressor under test is connected to the loop in a replaceable manner. The piping system is not disturbed during the compressor's swinging or tilting, resulting in high measurement accuracy and convenient and quick replacement of the compressor under test. Attached Figure Description

[0019] Figure 1 This is a schematic diagram of a three-dimensional structure for a test bench for the operation of air conditioning in new energy vehicles. Figure 2 A three-dimensional structural diagram of the compressor regulating component; Figure 3 A schematic diagram of the planar structure of the compressor regulating assembly; Figure 4 This is a three-dimensional structural diagram of the angle adjustment component; Figure 5 A three-dimensional structural diagram of the positioning component; Figure 6 This is a schematic diagram of the planar structure of the elastic load component; In the diagram: 1. Outer frame; 2. Controller; 3. Refrigerant circulation loop; 4. Compressor adjustment assembly; 41. Base; 42. Rotating shaft; 43. Angle adjustment assembly; 44. Positioning assembly; 45. Carrier plate; 46. Elastic load assembly; 431. First motor; 432. Rotating drum; 433. Limiting groove; 434. Swing arm; 435. Rotating wheel; 441. Mounting frame; 442. Second motor; 443. First gear; 444. First rack; 445. First clamping plate; 446. First guide seat; 447. Second gear; 448. Second clamping plate; 449. Second guide seat; 4410. Pressing column; 461. Bottom connecting seat; 462. Top connecting seat; 463. Limiting rod; 464. Slide; 465. Spring. Detailed Implementation

[0020] To make the objectives, technical solutions, and advantages of the present invention clearer, the various technical solutions of the present invention will be described in detail below with reference to the accompanying drawings. It should be noted that the terms "first," "second," etc., used below are only used to distinguish different components or parts, and do not constitute a limitation on the order, importance, or number of components or parts. The same reference numerals in the accompanying drawings indicate the same or similar components.

[0021] Before describing the various embodiments, some of the higher-level concepts and optional implementation methods involved in this invention are explained to facilitate understanding and implementation: First motor 431: can be either a servo motor or a stepper motor, preferably a servo motor with position feedback function, so as to achieve high-precision angle positioning and locking in precise angle mode.

[0022] The second motor 442 can be either a servo motor or a stepper motor, preferably a dual-output shaft servo motor capable of outputting dual-end drive torque.

[0023] Rotary cylinder 432: It is a cylindrical rotating body with the limiting groove 433 machined on its peripheral wall. The limiting groove 433 is a closed-loop groove structure.

[0024] Preload spring (located between the pressing post 4410 and the hole): Either a helical spring or a disc spring can be used.

[0025] Spring 465: Either a helical spring or a gas spring can be used.

[0026] Condenser: Any of the following can be used: plate heat exchanger, shell and tube heat exchanger or microchannel parallel flow heat exchanger.

[0027] Evaporator: Any of the following can be used: plate heat exchanger, shell and tube heat exchanger or microchannel parallel flow heat exchanger.

[0028] Electronic expansion valve: Either a needle valve type electronic expansion valve driven by a stepper motor or an electromagnetic electronic expansion valve can be used.

[0029] Mass flow meter: Coriolis mass flow meter is preferred, as it has high measurement accuracy under low flow conditions.

[0030] Refrigerant: Any one of R134a, R1234yf, R744 or R290 can be selected.

[0031] Example: In this embodiment of the invention, please refer to... Figures 1-6 A test bench for the operation of air conditioning in new energy vehicles is provided, comprising: an outer frame 1, a refrigerant circulation loop 3, a controller 2, and a compressor regulating component 4.

[0032] The outer frame 1, serving as the main load-bearing structure of the entire test bench, can be constructed from welded or bolted steel sections (such as square steel pipes or channel steel). Its internal space is divided into a refrigerant circuit installation area and a compressor testing area. The refrigerant circulation circuit 3 is fixedly integrated within the outer frame 1 and includes, in a closed loop following the refrigerant flow direction: a condenser, a mass flow meter, an electronic expansion valve, an evaporator, and piping connecting these components. It is important to note that the refrigerant circulation circuit 3 is not a complete circuit; it has two pre-reserved interfaces (a discharge interface and a suction interface). These interfaces are used to connect to the discharge and suction ports of the compressor under test, respectively, thus connecting the external compressor under test into the circuit to form a complete refrigeration cycle. All components in this circuit except the compressor under test (condenser, mass flow meter, electronic expansion valve, evaporator, and all piping) are fixed within the outer frame 1. These components remain stationary when the compressor under test swings or tilts during subsequent testing. The controller 2 is configured to monitor the operating parameters of the refrigerant circulation loop 3; the compressor adjustment assembly 4 is disposed within the outer frame 1 and includes: a base 41 fixed within the outer frame 1; two symmetrically arranged rotating shafts 42 rotatably supported on the base 41, the axes of the rotating shafts 42 extending horizontally; a positioning assembly 44 disposed between the two rotating shafts 42 and configured to position the compressor under test between the two rotating shafts 42 and connect the compressor under test to the refrigerant circulation loop 3; and an angle adjustment assembly 43 configured to drive one of the rotating shafts 42 to rotate, thereby causing the compressor under test to reciprocate or tilt to a target angle and maintain it around the axis of the rotating shaft 42.

[0033] Before testing, the compressor under test is installed in the positioning assembly 44 and locked. Its exhaust port and suction port are connected to the reserved interfaces of the refrigerant circulation loop 3 via flexible hoses. The refrigerant circulation loop 3 is started, and the refrigerant circulates between the compressor, condenser, mass flow meter, electronic expansion valve, and evaporator. The controller 2 collects data (pressure, temperature, flow rate) from each sensor in real time to evaluate the compressor's refrigeration performance. When tilting or bumping tests are required, the angle adjustment assembly 43 drives the rotating shaft 42 to rotate, and the compressor under test swings or tilts around the horizontal axis along with the positioning assembly 44.

[0034] In this embodiment, the compressor adjustment component 4 further includes a carrier plate 45, which is located below the positioning component 44 and connected to the positioning component 44 via an elastic load component 46. Specifically, the carrier plate 45 is disposed in the area directly below the clamping space of the positioning component 44, and the elastic load component 46 is connected between the carrier plate 45 and the positioning component 44: the upper end of the elastic load component 46 is connected to the bottom of the positioning component 44, and the lower end is connected to the upper surface of the carrier plate 45.

[0035] The carrier plate 45 is configured to support the compressor under test and can adjust the height of the compressor under test in the vertical direction so that the internal oil suction port of the compressor under test corresponds to the axis of the rotating shaft 42 in height position, and then the positioning component 44 locks and positions the compressor under test.

[0036] The purpose of this height adjustment is to align the oil suction port inside the compressor under test with the axis of the rotating shaft 42 in terms of height. It is necessary to clearly define the meaning of "oil suction port" in this invention. Electric compressors (taking scroll compressors as an example) do not have a separate oil suction pipe extending into the oil sump; the delivery of refrigerant oil inside relies on the centrifugal pump effect generated by the eccentric oil passage at the lower end of the main shaft during rotation. The "oil suction port" refers to the oil inlet area at the lower end of the main shaft used to draw in refrigerant oil. This area is located at the lowest point of the main shaft and is usually at a fixed vertical distance from the mounting surface of the compressor. This distance can be obtained from the three-dimensional digital model of the compressor or measured by industrial CT scanning. Adjusting the axis of the rotating shaft 42 to correspond in height with this oil inlet area (i.e., both are at the same horizontal level or approximately the same horizontal level) ensures that the vertical height of the oil inlet area remains essentially unchanged when the compressor is tilted around this axis; only the tilt angle of the oil sump changes. Therefore, the test results directly reflect the compressor's internal oil sump design's ability to resist tilting and oil shortage, eliminating interference caused by differences in the installation geometry of different compressors (different casing heights lead to different distances from the oil inlet area to the rotating shaft).

[0037] After the height of the carrier plate 45 is adjusted, the positioning component 44 locks and positions the compressor under test. At this time, the vertical position of the compressor under test is constrained by the carrier plate 45 and the positioning component 44.

[0038] In this embodiment, the angle adjustment component 43 includes: A rotating drum 432 is rotatably mounted on the base 41 and driven by a first motor 431. A limit groove 433 is provided on the peripheral wall of the rotating drum 432. The swing arm 434 has one end fixedly connected to the corresponding rotating shaft 42, and the other end rotatably connected to a rotating wheel 435. The rotating wheel 435 is constrained within the limiting groove 433. The extension trajectory of the limiting groove 433 is configured such that when the rotating drum 432 rotates continuously in one direction, the rotating wheel 435 moves cyclically along the limiting groove 433 and drives the swing arm 434 to swing back and forth around the axis of the rotating shaft 42, so as to simulate the dynamic disturbance of road bumps to the internal oil circuit of the compressor when the vehicle is driving.

[0039] The swing arm 434 is a long, strip-shaped rod (e.g., a metal rod with a rectangular or circular cross-section). One end of the swing arm 434 is fixedly connected to the corresponding rotating shaft 42 via a key connection, spline connection, or flange connection, preventing relative rotation between the swing arm 434 and the rotating shaft 42. The other end (free end) of the swing arm 434 is rotatably connected to a wheel 435 via a pin. The wheel 435 can be the outer ring of a rolling bearing or an independent roller.

[0040] During assembly, the rotating wheel 435 is embedded in the limiting groove 433. The extension trajectory of the limiting groove 433 is designed such that when the rotating drum 432 rotates continuously in one direction, the rotating wheel 435 moves cyclically along the trajectory of the limiting groove 433. The position of the rotating wheel 435 in the limiting groove 433 changes periodically with the deviation of the trajectory, thereby converting the displacement of the rotating wheel 435 into the angular displacement of the rotating shaft 42 through the swing arm 434, that is, driving the swing arm 434 to reciprocate around the axis of the rotating shaft 42. This reciprocating oscillation drives the rotating shaft 42, the positioning component 44, and the compressor under test, which are fixed to it, to reciprocate around the horizontal axis. The frequency of this reciprocating oscillation is determined by the rotational speed of the first motor 431, and the amplitude is determined by the trajectory geometry of the limiting groove 433. The reciprocating oscillation simulates the actual posture changes of the compressor when the vehicle is driving on a bumpy road. The pitching motion of the vehicle on the bumpy road causes the compressor housing to tilt and straighten continuously in the longitudinal direction. The oil level in the oil sump shakes violently with the bumps, posing the most severe dynamic test to the oil supply in the oil inlet area at the lower end of the main shaft.

[0041] Furthermore, the extension trajectory of the limiting groove 433 is also configured such that the maximum angle of the swing arm 434 swinging from the horizontal position to one side is 5° to 25°, preferably 20°; The first motor 431 is configured to have a reciprocating oscillation mode and a precise angle mode: In the reciprocating swing mode, the first motor 431 drives the rotating drum 432 to rotate continuously, and the swing arm 434 swings back and forth between 0° and the maximum angle. In the precise angle mode, the first motor 431 drives the rotating drum 432 to rotate to a specified angle and locks it, so that the compressor under test is kept at the corresponding tilt angle.

[0042] In the reciprocating swing mode, the first motor 431 drives the drum 432 to rotate continuously at a constant speed, and the swing arm 434 swings back and forth between 0° and the aforementioned maximum angle. Each rotation of the drum 432 completes one full reciprocating cycle for the swing arm 434. This mode is used to simulate the dynamic disturbance of road bumps on the internal oil circuit of the compressor.

[0043] In precise angle mode, the first motor 431 drives the drum 432 to rotate to a specific angular position and locks it in that position using the motor's brake function. At this time, the swing arm 434 is held at the corresponding tilt angle. By controlling different rotation angles of the drum 432, the swing arm 434 can be stopped at any specified angle between 0° and the maximum angle. This mode is used to gradually and accurately determine the static critical angle at which the compressor begins to experience oil shortage after dynamic bumps expose oil shortage.

[0044] In this embodiment, the positioning component 44 includes: Mounting frame 441, the middle of which has a through groove running vertically through it, for the compressor under test to pass through; The second motor 442 is fixed to one side of the mounting frame 441. The second motor 442 has a first driving end and a second driving end. The first driving end is coaxially fixed with a first gear 443. The first rack 444 is slidably disposed on one side of the mounting frame 441 and meshes with the first gear 443; The first clamping plate 445 is fixed to the end of the first rack 444 away from the first gear 443; The first guide seat 446 is fixed on the mounting frame 441 and provides sliding guidance for the first clamping plate 445 through the first guide rod.

[0045] In addition, a second gear 447 is coaxially fixed to the second drive end, the second gear 447 meshes with the second rack, and a second clamping plate 448 is fixed to the end of the second rack away from the second gear 447; a second guide seat 449 is fixed to the opposite side of the mounting frame 441, and the second guide seat 449 provides sliding guidance for the second clamping plate 448 through the second guide rod.

[0046] When the second motor 442 rotates, its first drive end and second drive end rotate synchronously. The first gear 443 and the second gear 447 synchronously drive the first rack 444 and the second rack to make linear movements in opposite directions. The first clamping plate 445 and the second clamping plate 448 move towards the center at the same time, clamping the compressor under test symmetrically from the left and right sides.

[0047] In this embodiment, both the first clamping plate 445 and the second clamping plate 448 have multiple holes, and each hole has a pressing post 4410 that slides through it. A pre-tensioning spring is connected between the pressing post 4410 and the hole. When the first clamping plate 445 and the second clamping plate 448 clamp the compressor under test, each pressing post 4410 elastically presses against the outer surface of the compressor under test under the action of the pre-tensioning spring.

[0048] The holes, which are either blind or through holes, are arranged in an array or staggered pattern on the clamping surface of the clamping plate. A pressing pin 4410 slides through each hole. The pressing pin 4410 is a short cylinder (e.g., a pin made of steel or copper), and its end facing the compressor housing may have a chamfer or a spherical surface to provide smooth contact. A preload spring, such as a coil spring, connects the pressing pin 4410 to the bottom or inner wall of the hole. One end of the preload spring abuts against the bottom of the hole, and the other end abuts against the inner end face of the pressing pin 4410. When the compressor is not clamped, the preload spring pushes the pressing pin 4410 outward to a maximum extended position (limited by a limiting structure to prevent the pressing pin 4410 from falling out of the hole).

[0049] When the first clamping plate 445 and the second clamping plate 448 move closer to and clamp the compressor housing, the outer ends of each pressing pin 4410 first contact the surface of the compressor housing. As the clamping plates continue to advance, the pressing pin 4410 that first contacts the housing is pressed into the hole, compressing the preload spring; the pressing pins 4410 that have not yet contacted the housing continue to extend until their outer ends also contact the housing surface. Finally, all the pressing pins 4410 independently press against the surface of the compressor housing under the elastic force of their respective preload springs.

[0050] In this embodiment, the elastic load component 46 includes: Bottom connecting seat 461 and top connecting seat 462, the top connecting seat 462 having a notch in the middle; Multiple limiting rods 463 are connected between the bottom connecting seat 461 and the top connecting seat 462; The slide block 464 passes through the notch and is slidably connected to each of the limiting rods 463; At least one spring 465 is connected between the bottom connecting seat 461 and the slide 464.

[0051] During implementation, the compressor under test is placed on the upper surface of the carrier plate 45. The compressor under test compresses the spring 465 by gravity. After the slide 464 slides down a certain distance along the limit rod 463, the compressor under test is locked by the positioning component 44.

[0052] In this embodiment, a discharge pressure sensor and a discharge temperature sensor are installed on the pipeline between the discharge port of the compressor under test and the condenser; a suction pressure sensor and a suction temperature sensor are installed on the pipeline between the refrigerant side outlet of the evaporator and the suction port of the compressor under test. The discharge pressure and discharge temperature directly reflect the working load and discharge state of the compressor under test under a given operating condition; the suction pressure and suction temperature reflect the refrigerant state at the evaporator outlet and the refrigerant parameters returning to the compressor. During tilt and bump tests, if the compressor under test experiences oil shortage, the friction between its internal scroll plate and bearings increases sharply, the discharge temperature will show a significant upward trend, and the input current will also fluctuate significantly due to the increased frictional torque.

[0053] Based on this, this embodiment also provides a test method for the critical angle of compressor tilt and oil shortage, including the following steps: S1: Place the compressor under test on the carrier plate 45, adjust the height of the carrier plate 45 so that the internal oil suction port of the compressor under test corresponds to the axis of the rotating shaft 42 in height position, lock the compressor under test by the positioning component 44, and connect the compressor under test to the refrigerant circulation loop 3; S2: Start the refrigerant circulation loop 3 when the compressor under test is in a 0° position, and run it to a thermal steady state; S3: Switch the first motor 431 to the reciprocating swing mode, drive the drum 432 to rotate continuously, and make the swing arm 434 drive the compressor under test to swing back and forth between 0° and the maximum angle to simulate the road bumps when the vehicle is driving. S4: During the reciprocating oscillation process, the exhaust temperature and input current of the compressor under test are continuously collected. When the rate of increase of the exhaust temperature exceeds the first threshold or the fluctuation amplitude of the input current exceeds the second threshold, it is determined that the compressor under test is short of oil under dynamic turbulence conditions, recorded as dynamic oil shortage, and S5 is executed. If the dynamic oil shortage does not occur after the reciprocating oscillation continues for a preset time, it is determined that the tilt tolerance of the compressor under test is qualified, and the test ends. S5: Switch the first motor 431 to the precise angle mode, so that the compressor under test returns to the 0° attitude and restarts to the thermal steady state; S6: The tilt angle of the compressor under test is gradually increased by the first motor 431 in a preset angle step, and a preset dwell time is maintained at each angle step, while the exhaust temperature and the input current are continuously collected; S7: When the rate of increase of the exhaust temperature exceeds the first threshold or the fluctuation of the input current exceeds the second threshold, the current tilt angle is recorded as the static critical tilt angle of the compressor under test, and the first motor 431 is immediately controlled to restore the compressor under test to the 0° attitude.

[0054] The above description is merely a preferred embodiment of the present invention, but the scope of protection of the present invention is not limited thereto. Any equivalent substitutions or modifications made by those skilled in the art within the scope of the technology disclosed in the present invention, based on the technical solution and inventive concept of the present invention, should be covered within the scope of protection of the present invention.

Claims

1. A test bench for the operation of air conditioning in new energy vehicles, characterized in that, include: Outer frame (1); The refrigerant circulation loop (3) is fixedly integrated within the outer frame (1) and includes the following components connected in a closed loop in the direction of refrigerant flow: condenser, mass flow meter, electronic expansion valve, evaporator, and pipelines connecting the above components. The controller (2) is configured to monitor the operating parameters of the refrigerant circulation loop (3); A compressor regulating assembly (4), disposed within the outer frame (1), includes: The base (41) is fixed inside the outer frame (1); Two symmetrically arranged rotating shafts (42) are rotatably supported on the base (41), and the axis of the rotating shafts (42) extends in the horizontal direction; The positioning component (44) is disposed between the two rotating shafts (42) and configured to position the compressor under test between the two rotating shafts (42) and connect the compressor under test to the refrigerant circulation loop (3). An angle adjustment component (43) is configured to drive one of the shafts (42) to rotate, thereby causing the compressor under test to reciprocate or tilt to a target angle and maintain it about the axis of the shaft (42).

2. The test bench according to claim 1, characterized in that, The compressor regulating assembly (4) also includes a carrier plate (45), which is located below the positioning assembly (44) and is connected to the positioning assembly (44) via an elastic load assembly (46); The carrier plate (45) is configured to support the compressor under test and can adjust the height of the compressor under test in the vertical direction so that the internal oil suction port of the compressor under test corresponds to the axis of the rotating shaft (42) in height position, and then the positioning component (44) locks and positions the compressor under test.

3. The test bench according to claim 1, characterized in that, The angle adjustment component (43) includes: A rotating drum (432) is rotatably mounted on the base (41) and driven by a first motor (431). A limiting groove (433) is provided on the peripheral wall of the rotating drum (432). A swing arm (434) has one end fixedly connected to the corresponding rotating shaft (42) and the other end rotatably connected to a rotating wheel (435). The rotating wheel (435) is constrained within the limiting groove (433). The extension trajectory of the limiting groove (433) is configured such that when the rotating drum (432) rotates continuously in one direction, the rotating wheel (435) moves cyclically along the limiting groove (433) and drives the swing arm (434) to swing back and forth around the axis of the rotating shaft (42) to simulate the dynamic disturbance of the road bumps on the internal oil circuit of the compressor when the vehicle is driving.

4. The test bench according to claim 3, characterized in that, The extension trajectory of the limiting groove (433) is also configured such that the maximum angle at which the swing arm (434) swings from the horizontal position to one side is 5° to 25°. The first motor (431) is configured to have a reciprocating oscillation mode and a precise angle mode: In the reciprocating swing mode, the first motor (431) drives the rotating drum (432) to rotate continuously, and the swing arm (434) swings back and forth between 0° and the maximum angle; In the precise angle mode, the first motor (431) drives the drum (432) to rotate to a specified angle and locks it, so that the compressor under test is kept at the corresponding tilt angle.

5. The test bench according to claim 1, characterized in that, The positioning component (44) includes: Mounting frame (441), the middle of which has a through groove that runs vertically through the compressor under test; The second motor (442) is fixed to one side of the mounting frame (441). The second motor (442) has a first driving end and a second driving end. The first driving end is coaxially fixed with a first gear (443). The first rack (444) slides through one side of the mounting frame (441) and meshes with the first gear (443); The first clamping plate (445) is fixed to the end of the first rack (444) away from the first gear (443); The first guide seat (446) is fixed on the mounting frame (441) and provides sliding guidance for the first clamping plate (445) through the first guide rod.

6. The test bench according to claim 5, characterized in that, The second drive end is coaxially fixed with a second gear (447), which meshes with a second rack. A second clamping plate (448) is fixed at one end of the second rack away from the second gear (447). A second guide seat (449) is fixed on the opposite side of the mounting frame (441), and the second guide seat (449) provides sliding guidance for the second clamping plate (448) through a second guide rod.

7. The test bench according to claim 6, characterized in that, Both the first clamping plate (445) and the second clamping plate (448) have multiple holes, and each hole has a pressing post (4410) that slides through it. A pre-tensioning spring is connected between the pressing post (4410) and the hole. When the first clamping plate (445) and the second clamping plate (448) clamp the compressor under test, each pressing post (4410) elastically presses against the outer surface of the compressor under test under the action of the pre-tensioning spring.

8. The test bench according to claim 2, characterized in that, The resilient load component (46) includes: Bottom connector (461) and top connector (462), the top connector (462) having a notch in the middle; Multiple limiting rods (463) are connected between the bottom connecting seat (461) and the top connecting seat (462); A slide (464) passes through the notch and is slidably connected to each of the limiting rods (463); At least one spring (465) is connected between the bottom connecting seat (461) and the slide (464).

9. The test bench according to claim 1, characterized in that, An exhaust pressure sensor and an exhaust temperature sensor are installed on the pipeline between the exhaust port of the compressor under test and the condenser; an intake pressure sensor and an intake temperature sensor are installed on the pipeline between the refrigerant side outlet of the evaporator and the intake port of the compressor under test.

Images