Compressors and refrigeration equipment

Abstract

The present application provides a compressor and a refrigeration device. The compressor includes a pump assembly and a drive motor, the pump assembly includes a rotating part and a fixed part, the drive motor is drivingly connected to the rotating part, the fixed part includes an air intake port and an air intake valve plate, the air intake valve plate is arranged at the air intake port of the pump assembly, and the interphase permanent magnet flux peak-to-peak value ψ f The range is: #imgabs0# where k w1 is the fundamental wave winding factor, P is the number of motor pole pairs, the stiffness of the suction valve plate ranges from 450 to 600 N / m, and the natural frequency of the suction valve plate ranges from 300 to 410 Hz. The compressor according to the present application can greatly increase the upper limit of the cooling capacity of the variable frequency piston compressor while keeping the displacement of the compressor unchanged, and greatly improve the energy efficiency of the whole machine.

Description

Technical Field

[0001] The present application relates to the technical field of refrigeration equipment, and in particular to a compressor and refrigeration equipment. Background Art

[0002] The inverter refrigerator compressor can run at a lower speed, solving the problems of frequent startup of traditional fixed-speed compressors, large temperature fluctuations in the freezing and refrigeration compartments, poor temperature control accuracy, and high power consumption. It has been widely promoted and popularized. From the actual use and refrigeration control process of the inverter refrigerator, when a new refrigerator is powered on for the first time or detects that the freezing temperature sensor is greater than 10°C and the refrigeration temperature sensor is greater than 15°C at any time, or when the user puts in quick-frozen food, there is a need for rapid refrigeration. At this time, the inverter piston compressor runs continuously at the highest frequency until the low-temperature program ends or the quick-freezing function exits. The traditional inverter piston compressor can only run at 75Hz (ie 4500rpm), and the cooling capacity provided is limited. It often needs to run at the highest operating frequency for 4 hours, or even longer, to meet the temperature control requirements of each compartment. The relatively long low-temperature or quick-freezing time affects the freshness of food in the refrigerator, especially seafood and fruits.

[0003] In addition, according to statistics, the proportion of time when large cooling capacity is required to the user's refrigerator usage time is about 15-25%, and the rest is medium and low load operation. Therefore, it is not suitable to use a large-displacement traditional variable-frequency compressor to meet short-term large cooling capacity needs. This will only increase the total power consumption and the cost of the compressor. In addition, the large-displacement traditional variable-frequency piston compressor occupies a larger space in the refrigerator as a whole, which in turn affects the overall layout and storage space inside the refrigerator.

[0004] How to achieve the goal of maintaining the compressor displacement unchanged or even increasing the displacement while significantly increasing the upper limit of the cooling capacity of the variable frequency piston compressor is a technical problem that is difficult to solve in the current compressor field. Summary of the invention

[0005] Therefore, the technical problem to be solved by the present application is to provide a compressor and a refrigeration device, which can significantly increase the upper limit of the cooling capacity of the variable frequency piston compressor while keeping the displacement of the compressor unchanged, and significantly improve the energy efficiency of the whole machine.

[0006] In order to solve the above problems, the present application provides a compressor, including a pump body assembly and a drive motor, the pump body assembly includes a rotating part and a fixed part, the drive motor is connected to the rotating part, the fixed part includes an air intake port and an air intake valve plate, the air intake valve plate is arranged at the air intake port of the pump body assembly, and the interphase permanent magnet flux peak-to-peak value ψ of the drive motor is f The range is:

[0007]

[0008] where kw1 is the fundamental wave winding factor, P is the number of motor pole pairs, the stiffness of the intake valve plate ranges from 450 to 600 N / m, and the natural frequency of the intake valve plate ranges from 300 to 410 Hz.

[0009] Preferably, the drive motor includes a rotor assembly and a stator assembly, the rotor assembly includes a rotor core and magnetic steel, and the magnetic steel is attached to the outer peripheral wall of the rotor core.

[0010] Preferably, the outer peripheral wall of the rotor core is provided with a plurality of convex strips along the circumferential direction, each convex strip extends along the axial direction of the rotor core, and mounting grooves are formed between adjacent convex strips, and the magnetic steel is installed in the mounting grooves. The stator assembly includes a stator core, and a rotor mounting hole is provided in the stator core, and the rotor assembly is arranged in the rotor mounting hole.

[0011] Preferably, at least one end of the magnetic steel extends out of the stator core in the axial direction, and the length L extending out of the stator core is in the range of 3mm≤L≤5mm.

[0012] Preferably, the ratio of the maximum radial thickness H of the magnetic steel to the maximum outer diameter D2 of the magnetic steel is in the range of 0.22≤2H / D2≤0.26.

[0013] Preferably, the ratio of the width H1 of the teeth of the stator core to the minimum width H2 of the yoke satisfies 1.3≤H1 / H2≤1.5.

[0014] Preferably, a stator winding is provided on the stator core, and the diameter of the coil of the stator winding with paint is greater than or equal to 0.63 mm.

[0015] Preferably, the air gap δ between the stator assembly and the rotor assembly is ≤ 0.35 mm.

[0016] Preferably, the effective value of the back EMF of the motor is e, and the back EMF coefficient Ke=e / (0.128*n*P), with the unit of V / (rad / s), where n is the speed corresponding to the back EMF e, P is the number of motor poles, and Ke satisfies:

[0017] 0.06≤Ke≤0.078.

[0018] Preferably, in a cross section perpendicular to the central axis of the rotor core, the outer peripheral side of the magnetic steel includes a first arc segment and a first trimming segment located at both ends of the first arc segment, the angle between the first trimming segment and the radial center line of the magnetic steel is α, the center angle of the first arc segment is β, the stator core includes a tooth shoe, the inner peripheral wall of the tooth shoe includes a second arc segment and a second trimming segment located at both ends of the second arc segment, the center angle of the second arc segment is λ, wherein 0.59≤sinβ / sinα≤0.6; 1.745≤sinβ / sinλ≤1.755.

[0019] Preferably, in a cross section perpendicular to the central axis of the rotor core, the outer peripheral side of the magnetic steel includes a first arc segment and a first trimming segment located at both ends of the first arc segment, and the angle between the first trimming segment and the radial center line of the magnetic steel is α, where 58.5°≤α≤60.5°.

[0020] Preferably, the thickness of the stator punching sheets of the stator core and / or the rotor punching sheets of the rotor core is less than or equal to 0.35 mm.

[0021] Preferably, when the displacement of the compressor is 8.0-9.0cc, the maximum speed of the drive motor is greater than or equal to 6000rpm, when the displacement of the compressor is 7.0-8.0cc, the maximum speed of the drive motor is greater than or equal to 6600rpm, and when the displacement of the compressor is 6.0-7.0cc, the maximum speed of the drive motor is greater than or equal to 7200rpm.

[0022] According to another aspect of the present application, a refrigeration device is provided, comprising a compressor, which is the above-mentioned compressor.

[0023] The compressor provided in the present application comprises a pump body assembly and a drive motor, wherein the pump body assembly comprises a rotating part and a fixed part, the drive motor is drivingly connected to the rotating part, the fixed part comprises an air intake port and an air intake valve plate, the air intake valve plate is arranged at the air intake port of the pump body assembly, and the interphase permanent magnet flux peak-to-peak value ψ f The range is: where k w1 is the winding factor, P is the number of motor poles, the stiffness of the air intake valve is in the range of 450-600N / m, and the natural frequency of the air intake valve is in the range of 300-410Hz. frange, can provide the optimal permanent magnet flux linkage range, thereby changing the flux linkage value, so that the permanent magnet flux linkage is within a reasonable range, reducing the output voltage limit on the maximum speed of the motor, so that the compressor can break through the traditional compressor efficient operation range and the upper limit speed limit, and achieve high efficiency operation of the motor within a predetermined speed range, so that the compressor provides maximum cooling capacity when the motor is running at the highest speed, thereby achieving a significant expansion of the upper limit of cooling capacity under the same displacement, and achieving a reduction of more than 20% in the low temperature or quick freezing time when a new refrigerator is powered on for the first time or when food needs to be quickly frozen. Due to the increase in motor speed, the operating frequency of the compressor is greatly increased, and the structural performance of the intake valve plate cannot match the increase in the compressor frequency. Therefore, in order to meet the requirements of significantly shortening the low temperature or quick freezing time of the refrigerator, the present application optimizes the stiffness and natural frequency of the intake valve plate, which can meet the requirements that the intake and exhaust valve plates follow the motor speed when the motor is running at high speed and close in time, ensuring that the cooling capacity is not attenuated during high-speed operation, or even increased, and the intake and exhaust loss work is low. By adopting the compressor of the present application, it is possible to achieve a 20-25% reduction in displacement and an unchanged maximum output cooling capacity under the same pump body structure platform; or the compressor displacement remains unchanged and the maximum output cooling capacity can be increased to more than 1.3 times. BRIEF DESCRIPTION OF THE DRAWINGS

[0024] Figure 1 This is a schematic diagram of a first structure of a stator core of a drive motor of a compressor according to an embodiment of the present application;

[0025] Figure 2 A second structural schematic diagram of a stator core of a drive motor of a compressor according to an embodiment of the present application;

[0026] Figure 3 This is a schematic structural diagram of a rotor core of a drive motor of a compressor of an embodiment of the present application;

[0027] Figure 4 This is a schematic diagram of the three-dimensional structure of the rotor core of the drive motor of the compressor of the embodiment of the present application;

[0028] Figure 5 A diagram comparing the output torque of the compressor of the embodiment of the present application and the compressor in the prior art;

[0029] Figure 6 A corresponding curve diagram of the maximum cooling capacity and the suction valve plate stiffness of the compressor of the embodiment of the present application at 120 Hz;

[0030] Figure 7 It is a schematic diagram of the structure of the voltage limit ellipse and the current limit circle of the compressor of the embodiment of the present application;

[0031] Figure 8 This is a comparison chart of low temperature tests of the compressor according to the embodiment of the present application and a traditional compressor.

[0032] The reference numerals are:

[0033] 1. Rotor core; 2. Magnetic steel; 3. Raised strip; 4. Stator core; 5. First arc segment; 6. First trimming segment; 7. Second arc segment; 8. Second trimming segment; 9. Tooth shoe. DETAILED DESCRIPTION

[0034] See also Figures 1 to 8 As shown, according to an embodiment of the present application, the compressor includes a pump body assembly and a drive motor, the pump body assembly includes a rotating part and a fixed part, the drive motor is drivingly connected to the rotating part, the fixed part includes an air intake port and an air intake valve plate, the air intake valve plate is arranged at the air intake port of the pump body assembly, and the interphase permanent magnet flux peak-to-peak value ψ of the drive motor f The range is:

[0035]

[0036] where k w1 is the fundamental wave winding factor, P is the number of motor pole pairs, the stiffness of the intake valve plate ranges from 450 to 600 N / m, and the natural frequency of the intake valve plate ranges from 300 to 410 Hz.

[0037] By limiting the peak-to-peak value of the interphase permanent magnet flux linkage of the drive motor ψ f range, can provide the optimal permanent magnet flux linkage range, thereby changing the flux linkage value, so that the permanent magnet flux linkage is within a reasonable range, reducing the output voltage and output current restrictions on the maximum speed of the motor, so that the compressor can break through the restrictions of the traditional compressor's efficient operating range and upper limit speed, and realize the motor's high-efficiency operation within a predetermined speed range, so that the compressor provides the maximum cooling capacity when the motor is running at the highest speed, thereby being able to achieve a significant expansion of the upper limit of cooling capacity under the same displacement, and realizing that when a new refrigerator is first powered on or food needs to be quickly frozen, the low temperature or quick freezing time is shortened by more than 20%. Due to the increase in motor speed, the operating frequency of the compressor is greatly increased, and the performance of the intake valve plate cannot match the increase in the compressor frequency. Therefore, in order to meet the requirements for significantly shortening the low temperature or quick freezing time of the refrigerator, the present application optimizes the stiffness and natural frequency of the intake valve plate, which can meet the requirements that the intake and exhaust valve plates follow the motor speed when the motor is running at high speed and close in time, ensuring that the high-speed operation cooling capacity is not attenuated, or even improved, and the intake and exhaust loss work is low. By adopting the compressor of the present application, it is possible to achieve a 20-25% reduction in displacement and an unchanged maximum output cooling capacity under the same pump body structure platform; or the compressor displacement remains unchanged and the maximum output cooling capacity can be increased to more than 1.3 times.

[0038] If you want to improve the maximum speed and rated energy efficiency of variable frequency piston compressors, you need to solve two key problems:

[0039] (1) Due to the limit values ​​of the output voltage and output current of the frequency converter, if you want to run at a higher frequency, the permanent magnet flux of the permanent magnet synchronous motor needs to be reduced, resulting in a decrease in the maximum output torque and the motor efficiency.

[0040] (2) When the compressor pump body is operated at a higher speed than traditional compressors, the original suction and exhaust valve plate suction and exhaust loss work increases and cannot be opened and closed in time, causing the compressor power consumption and cooling capacity to deteriorate, and the energy efficiency of the whole machine to drop significantly.

[0041] Therefore, if you want to increase the maximum operating speed and rated point energy efficiency of the compressor, you need to consider both the magnetic flux and the suction valve plate.

[0042] The variable frequency piston compressor motor is generally a hidden pole permanent magnet synchronous motor with a surface mounted rotor structure. The d-axis and q-axis inductances are similar. At the same time, the variable frequency controller often uses the control mode of id = 0. According to the electromagnetic torque formula T em =Pψ f i q +p(L d -L q )i d i q , we know that the magnetic resistance torque is 0, so the motor output electromagnetic torque T em With permanent magnet flux ψ f Directly related to optimizing permanent magnet flux linkage ψ f The optimal output torque can be achieved.

[0043] In addition, frequency converters usually follow the voltage limit ellipse and current limit circle ( Figure 2 ), the intersection of the voltage limit circle and the current limit circle is the operating range of the motor. It can be seen that when the voltage and current at the output end of the controller are limited, the speed has a maximum speed.

[0044] The present application optimizes the magnetic flux and reduces the back EMF by reducing the magnetic flux. After the back EMF is reduced, as the motor speed increases, the back EMF corresponding to the maximum speed is lower than before optimization. Therefore, when the back EMF reaches the limit value, the motor speed can reach a higher speed value. In this way, it is possible to effectively break through the limitations of traditional compressors, greatly increase the upper limit of the motor speed, thereby increasing the operating frequency of the compressor, breaking through the high-efficiency operating range and upper limit speed of traditional variable frequency piston compressors, and achieving a large high-efficiency range of the motor within a predetermined speed range. The maximum efficiency point is improved, and the maximum operating speed can reach 7200rpm, i.e. 120Hz, and the upper limit of cooling capacity is greatly widened under the same displacement.

[0045] For example, before reducing the magnetic flux, the back EMF at 1000 rpm is 10 V, and at 7200 rpm it is 72 V. After the reduction, it is 5 V at 1000 rpm and 36 V at 7200 rpm. Thus, the back EMF can be reduced, so that the maximum speed can be effectively improved.

[0046] This application is also based on the research of various parts of the compressor pump body, especially the changes in the stiffness and natural frequency of the suction and exhaust valve plate, the impact on the suction and exhaust power loss, dynamic response capability and reflux rate, and proposes an optimal suction and exhaust valve parameter with the goal of not attenuating the cooling capacity under high-speed conditions. In this way, the compressor of this application has a widened maximum operating speed range, and the overall energy efficiency of the machine has been greatly improved compared with traditional variable frequency piston compressors.

[0047] This application is based on long-term research on compressor pump body structural parameters and motor parameters and a large number of experiments, and obtains the corresponding relationship between compressor pump body structural parameters and motor parameters that meets the wide frequency band operation. The motor and its compressor designed based on this parameter chain relationship can achieve a maximum speed that is 1.7 times that of traditional compressors.

[0048] By optimizing the magnetic flux operating range and the structure of the intake valve plate, high-speed operation can be achieved under voltage and current limitations. At the same time, the motor's high-efficiency range area is large within the predetermined speed range, and the maximum efficiency point is improved.

[0049] For this type of high-speed variable-frequency piston compressor, research and a large amount of test data show that the cooling capacity in the high-speed area is directly related to the stiffness of the suction valve plate. The optimal valve plate stiffness corresponding to the different high-speed application areas is different, and the suction and exhaust loss work can also be reduced.

[0050] Based on this analysis, combined with Figure 6 As shown, when the compressor operates at 120Hz, when the stiffness of the intake valve plate is greater than or equal to 450N / m, the cooling capacity output of the compressor basically does not change much. Therefore, the present application limits the stiffness range of the intake valve plate under high-speed operation to 450-600N / m, thereby ensuring that the compressor has a higher cooling capacity under high-frequency operating conditions and meets the cooling capacity output capacity of the compressor, while avoiding the performance waste caused by the excessive stiffness of the intake valve plate and excessively increasing the valve plate cost, thereby achieving a better balance between cost and performance.

[0051] By adopting the above-mentioned scheme of the present application, an optimal permanent magnet flux linkage range can be provided, so that the motor can operate efficiently within a predetermined speed range. In addition, maximum cooling capacity can be provided when operating at the highest speed. In order to meet the requirements of significantly shortening the low temperature or quick freezing time of the refrigerator, the stiffness and natural frequency of the intake valve plate are optimized to ensure that the intake and exhaust valve plates can close in time with the motor speed when the motor is running at high speed, ensuring that the cooling capacity is not attenuated during high-speed operation, and even improved, and the intake and exhaust loss work is low.

[0052] The driving motor comprises a rotor assembly and a stator assembly. The rotor assembly comprises a rotor core 1 and a magnetic steel 2 . The magnetic steel 2 is attached to the outer peripheral wall of the rotor core 1 .

[0053] In this embodiment, the outer wall of the rotor core 1 is provided with a plurality of convex strips 3 along the circumferential direction, each convex strip 3 extends along the axial direction of the rotor core 1, and a mounting groove is formed between adjacent convex strips 3, and the magnetic steel 2 is installed in the mounting groove. The stator assembly includes a stator core 4, and a rotor mounting hole is provided in the stator core 4, and the rotor assembly is arranged in the rotor mounting hole.

[0054] At least one end of the magnetic steel 2 extends out of the stator core 4 in the axial direction, and the length L extending out of the stator core 4 is in the range of 3mm≤L≤5mm.

[0055] For the drive motor, since the back EMF e=Ndφ / dt=dλ / dt, the factors that affect the motor's back EMF, in addition to the time-varying magnetic flux, are the number of coil turns N. If you want to reduce the back EMF, you can consider reducing the number of coil turns N. However, if the number of coil turns N is reduced, the magnetic flux will be reduced, and then the maximum output torque of the motor will be reduced. Therefore, in order to avoid a reduction in the output torque of the motor, the axial length of the magnetic steel 2 can be increased so that the magnetic steel 2 extends axially out of the stator core 4, thereby achieving a reduction in the back EMF on the basis of reducing the number of coil turns, thereby ensuring that the maximum speed of the motor can be effectively increased, and avoiding a reduction in magnetic flux, thereby ensuring the output torque of the motor and improving the working performance of the motor.

[0056] The ratio of the maximum radial thickness H of the magnetic steel 2 to the maximum outer diameter D2 of the magnetic steel 2 is in the range of 0.22≤2H / D2≤0.26.

[0057] The ratio between the width H1 of the teeth of the stator core 4 and the minimum width H2 of the yoke satisfies 1.3≤H1 / H2≤1.5.

[0058] Since the flux linkage value is generated by the magnetic flux generated by the rotor and the stator winding, the design of the flux linkage range needs to be considered comprehensively from both the stator and the rotor. From the rotor side, the size of the magnetic flux is directly related to the magnetic steel. The cutting edge of the magnetic steel determines the size of the torque pulsation, and the thickness of the magnetic steel determines the size of the magnetic flux that the stator winding can cross-link. Through simulation and experimental analysis, when the ratio of the thickness of the magnetic steel to the maximum radius of the magnetic steel is 0.22 to 0.26, the requirements of the phase-to-phase flux linkage value can be met. From the stator side, the size of the magnetic flux is directly related to the number of winding turns, and the size of the effective slot area of ​​the stator directly affects the number of winding turns. Under the premise that the shape of the motor has been determined, the proportion of the tooth width and the yoke width directly affects the slot area. Through analysis, it can be seen that when the ratio of the tooth width to the yoke width is 1.3 to 1.5, the range of the back electromotive force coefficient can be met.

[0059] The stator core 4 is provided with a stator winding, and the diameter of the coil of the stator winding with paint is greater than or equal to 0.63 mm. Because the stator slot area of ​​the motor is the same and the slot filling rate is unchanged, when the number of turns is reduced to reduce the magnetic flux, the winding wire diameter is increased accordingly, which can effectively ensure the slot filling rate of the stator winding.

[0060] The air gap between the stator assembly and the rotor assembly is δ≤0.35mm, that is, δ=(D1-D2) / 2≤0.35mm, which can effectively improve the motor torque output capacity. Figure 5 As shown, at a rated current of 0.9A, the motor with a 0.35mm air gap has an output torque that is 4% higher than that with a 0.5mm air gap.

[0061] The effective value of the back EMF of the motor is e, and the back EMF coefficient Ke=e / (0.128*n*P), with the unit of V / (rad / s), where n is the speed corresponding to the back EMF e, P is the number of motor poles, and Ke satisfies: 0.06≤Ke≤0.078.

[0062] By limiting the back-electromotive force coefficient, it can be ensured that the determined motor can meet the relationship of wide-band operation, so that the relationship between the back-electromotive force and the rotational speed can meet the requirement of high-speed operation of the motor.

[0063] For the present application, when the motor model is determined, the motor pole pair number P value is determined, and the factors that can affect the back-EMF coefficient are the back-EMF e and the speed n corresponding to the back-EMF e. Therefore, after limiting a reasonable back-EMF coefficient, the relationship between the back-EMF e and the speed n is inversely proportional at 1000rpm, and by controlling the motor magnetic flux, the back-EMF e can be effectively reduced. Accordingly, the motor speed n can be greatly increased to meet the speed requirements of the compressor during rapid cooling and meet the high-frequency operation requirements of the compressor.

[0064] When the motor speed n is determined, the back-EMF coefficient Ke is proportional to the back-EMF e. Therefore, it is necessary to limit the maximum value of Ke to avoid the back-EMF e being too large and thus limiting the motor speed. At the same time, when Ke is too small, the back-EMF may also be reduced, thereby reducing the number of coil turns, increasing the current, increasing the controller loss, and reducing the overall efficiency of the motor. Therefore, by reasonably limiting the upper and lower limits of the back-EMF coefficient Ke, it is possible to avoid the problem of too low back-EMF leading to excessive controller loss and reduced overall motor efficiency. At the same time, it is also possible to avoid the problem of the motor speed being unable to be effectively provided due to the back-EMF being too large. This can achieve a better balance between the motor speed and the motor working performance, thereby improving the overall energy efficiency of the motor.

[0065] In a cross section perpendicular to the central axis of the rotor core 1, the outer peripheral side of the magnetic steel 2 includes a first arc segment 5 and a first trimming segment 6 located at both ends of the first arc segment 5, the angle between the first trimming segment 6 and the radial center line of the magnetic steel 2 is α, the center angle of the first arc segment 5 is β, the stator core 4 includes a tooth shoe 9, the inner peripheral wall of the tooth shoe 9 includes a second arc segment 7 and a second trimming segment 8 located at both ends of the second arc segment 7, the center angle of the second arc segment 7 is λ, wherein 0.59≤sinβ / sinα≤0.6; 1.745≤sinβ / sinλ≤1.755.

[0066] By limiting the above structure, the torque ripple of the motor can be effectively reduced. Experiments have shown that within the limited range, the torque ripple can be effectively reduced from 17% to 2%.

[0067] In a cross section perpendicular to the central axis of the rotor core 1, the outer peripheral side of the magnetic steel 2 includes a first arc segment 5 and a first trimming segment 6 located at both ends of the first arc segment 5, and the angle between the first trimming segment 6 and the radial center line of the magnetic steel 2 is α, where 58.5°≤α≤60.5°.

[0068] By increasing the cut edge of the magnetic steel, it can cooperate with the cut edge on the stator core 4 to effectively reduce torque pulsation and reduce noise vibration caused by electromagnetic force.

[0069] Preferably, the thickness of the stator punching sheets of the stator core 4 and / or the rotor punching sheets of the rotor core 1 is less than or equal to 0.35 mm, which can effectively reduce iron loss and improve motor efficiency.

[0070] When the displacement of the compressor is 8.0-9.0cc, the maximum speed of the drive motor is greater than or equal to 6000rpm. When the displacement of the compressor is 7.0-8.0cc, the maximum speed of the drive motor is greater than or equal to 6600rpm. When the displacement of the compressor is 6.0-7.0cc, the maximum speed of the drive motor is greater than or equal to 7200rpm.

[0071] Since the cooling capacity of the compressor is affected by both the compressor displacement and the motor speed, if the cooling capacity of the compressor is to be kept unchanged, it is necessary to increase the motor speed when the compressor displacement decreases, and reduce the motor speed when the compressor displacement increases, so that a good match can be formed between the compressor displacement and the speed, thereby ensuring the cooling performance of the compressor.

[0072] The compressor of the present application is particularly suitable for refrigerant R600a, R134a or R290.

[0073] For kw1, when the slot-to-pole ratio of the motor is 3:2, kw1=0.866; when the slot-to-pole ratio is 6:5, kw1=0.933. Other slot-to-pole ratios are calculated according to the winding factor calculation method of known technology.

[0074] The compressor of the present application has a driving motor with a maximum rotation speed greater than or equal to 6000 rpm.

[0075] The maximum operating frequency of the compressor of the present application is greater than 80 Hz.

[0076] According to an embodiment of the present application, a refrigeration device includes a compressor, which is the above-mentioned compressor.

[0077] The refrigeration device is, for example, a refrigerator or a freezer.

[0078] It is easy for those skilled in the art to understand that the above-mentioned advantageous methods can be freely combined and superimposed without conflict.

[0079] The above are only preferred embodiments of the present application and are not intended to limit the present application. Any modifications, equivalent replacements and improvements made within the spirit and principles of the present application shall be included in the protection scope of the present application. The above are only preferred implementations of the present application. It should be pointed out that for ordinary technicians in this technical field, several improvements and variations can be made without departing from the technical principles of the present application, and these improvements and variations should also be regarded as the protection scope of the present application.

Claims

1. A compressor, characterized in that: The invention comprises a pump body assembly and a driving motor, wherein the pump body assembly comprises a rotating part and a fixed part, the driving motor is drivingly connected to the rotating part, the fixed part comprises an air intake port and an air intake valve plate, the air intake valve plate is arranged at the air intake port of the pump body assembly, and the interphase permanent magnet flux peak-to-peak value ψ f The range is: where k w1 is the fundamental wave winding factor, P is the number of motor pole pairs, the stiffness of the intake valve plate ranges from 450 to 600 N / m, the natural frequency of the intake valve plate ranges from 300 to 410 Hz; and the compressor is a variable frequency piston compressor.

2. The compressor according to claim 1, characterized in that The drive motor comprises a rotor assembly and a stator assembly, wherein the rotor assembly comprises a rotor core (1) and a magnetic steel (2), wherein the magnetic steel (2) is attached to the outer peripheral wall of the rotor core (1).

3. The compressor according to claim 2, characterized in that The outer peripheral wall of the rotor core (1) is provided with a plurality of convex strips (3) along the circumferential direction, each of the convex strips (3) extends along the axial direction of the rotor core (1), and a mounting groove is formed between adjacent convex strips (3), and the magnetic steel (2) is mounted in the mounting groove. The stator assembly comprises a stator core (4), and a rotor mounting hole is provided in the stator core (4), and the rotor assembly is arranged in the rotor mounting hole.

4. The compressor according to claim 3, characterized in that At least one end of the magnetic steel (2) extends out of the stator core (4) in the axial direction, and the length L of the extension from the stator core (4) is in the range of 3mm≤L≤5mm.

5. The compressor according to claim 2, characterized in that The ratio of the maximum radial thickness H of the magnetic steel (2) to the maximum outer diameter D2 of the magnetic steel (2) is in the range of 0.22≤2H / D2≤0.

26.

6. The compressor according to claim 3, characterized in that The ratio between the width H1 of the teeth of the stator core (4) and the minimum width H2 of the yoke satisfies 1.3≤H1 / H2≤1.

5.

7. The compressor according to claim 3, characterized in that The stator core (4) is provided with a stator winding, and the diameter of the coil of the stator winding with paint is greater than or equal to 0.63 mm.

8. The compressor according to claim 2, characterized in that The air gap δ between the stator assembly and the rotor assembly is ≤0.35 mm.

9. The compressor according to claim 2, characterized in that The effective value of the back EMF of the motor is e, and the back EMF coefficient Ke=e / (0.128*n*P), with the unit of V / (rad / s), where n is the speed corresponding to the back EMF e, P is the number of motor poles, and Ke satisfies: 0.06≤Ke≤0.

078.

10. The compressor according to claim 3, characterized in that In a cross section perpendicular to the central axis of the rotor core (1), the outer peripheral side of the magnetic steel (2) comprises a first arc segment (5) and a first trimming segment (6) located at two ends of the first arc segment (5), the angle between the first trimming segment (6) and the radial centerline of the magnetic steel (2) is α, the center angle of the first arc segment (5) is β, the stator core (4) comprises a tooth shoe (9), the inner peripheral wall of the tooth shoe (9) comprises a second arc segment (7) and a second trimming segment (8) located at two ends of the second arc segment (7), the center angle of the second arc segment (7) is λ, wherein 0.59≤sinβ / sinα≤0.6; 1.745≤sinβ / sinλ≤1.

755.

11. The compressor according to claim 2, characterized in that In a cross section perpendicular to the central axis of the rotor core (1), the outer peripheral side of the magnetic steel (2) comprises a first arc segment (5) and first trimming segments (6) located at both ends of the first arc segment (5), and the angle between the first trimming segment (6) and the radial centerline of the magnetic steel (2) is α, wherein 58.5°≤α≤60.5°.

12. The compressor according to claim 3, characterized in that The thickness of the stator punching sheets of the stator core (4) and / or the rotor punching sheets of the rotor core (1) is less than or equal to 0.35 mm.

13. The compressor according to claim 1, characterized in that When the displacement of the compressor is 8.0-9.0cc, the maximum speed of the drive motor is greater than or equal to 6000rpm; when the displacement of the compressor is 7.0-8.0cc, the maximum speed of the drive motor is greater than or equal to 6600rpm; when the displacement of the compressor is 6.0-7.0cc, the maximum speed of the drive motor is greater than or equal to 7200rpm.

14. A refrigeration device, comprising a compressor, characterized in that: The compressor is the compressor according to any one of claims 1 to 13.

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