Horizontal compressor and new energy automobile

Abstract

The invention provides a horizontal compressor and a new energy automobile, and the horizontal compressor comprises a first cavity which is defined by a middle shell and a front shell and is used for accommodating a motor, a dynamic vortex plate and a static vortex plate; the air inlet air suction pressing plate is arranged on the side, away from the dynamic vortex disc, of the motor and is in butt joint with the middle shell, the first side of the air inlet air suction pressing plate is provided with an annular flange protruding out of the middle shell and provided with an inward-shrinkage step-shaped air suction hole penetrating through the annular flange, and the inward-shrinkage step-shaped air suction hole comprises an outer-section air suction port and an inner-section air suction port; the rear shell and the second side of the air inlet air suction pressing plate define a second cavity for containing the power circuit module, the axis of the outer section air suction port and the axis of the inner section air suction port are not collinear, and the inner section air suction port guides refrigerant entering from the outer section air suction port to at least move in the direction close to the second cavity in the flowing process. Through the stepped variable-diameter structure of the air suction port, the flow speed of a refrigerant is increased, the cooling effect on the power circuit module is enhanced, and the efficiency of the compressor is improved.

Description

Technical Field

[0001] The present invention relates to the field of vehicle-mounted refrigeration equipment, and in particular to a horizontal compressor and a new energy vehicle. Background Art

[0002] In existing scroll compressors, in certain application scenarios, the refrigerant suction flow rate flowing back to the compressor from the air conditioning system is very small, or the suction temperature is very high. At this time, the heat dissipation effect on the controller is poor, which can easily cause the controller to overheat and fail. Such scenarios include: low compressor speed and high load operation conditions; ultra-low temperature heat pump conditions (the mass flow rate of the refrigerant is very small); low compressor speed but high suction superheat conditions.

[0003] The existing solutions basically adopt the method of adding a deflector cover to optimize the heat dissipation of the controller, which requires additional parts and has a complex installation structure.

[0004] In view of this, the present invention provides a horizontal compressor and a new energy vehicle. Summary of the invention

[0005] In response to the problems in the prior art, the horizontal compressor and new energy vehicle of the present invention overcome the difficulties of the prior art and can accelerate the refrigerant flow rate through the stepped variable diameter structure of the air intake port without adding additional parts, thereby enhancing the cooling effect on the power circuit module and improving the compressor efficiency.

[0006] An embodiment of the present invention provides a compressor suspension assembly, comprising:

[0007] The middle shell and the front shell together form a first cavity for accommodating the motor, the movable scroll and the fixed scroll;

[0008] An air inlet suction pressure plate is arranged on a side of the motor away from the movable scroll and docked with the middle shell. A first side of the air inlet suction pressure plate is provided with an annular flange protruding from the middle shell, and an inwardly contracted step-type air inlet hole passing through the annular flange is provided. The inwardly contracted step-type air inlet hole includes an outer section air inlet connected to each other and an inner section air inlet having a diameter smaller than that of the outer section air inlet;

[0009] The rear shell and the second side of the air inlet suction pressure plate together form a second cavity for accommodating the power circuit module. The axis of the outer air inlet and the axis of the inner air inlet are not colinear. The inner air inlet guides the refrigerant entering from the outer air inlet to at least move in a direction close to the second cavity during the flow process.

[0010] Preferably, the relationship between the diameter D1 of the outer section air intake port and the diameter D2 of the inner section air intake port is: 0.53≤D2 / D1≤0.68.

[0011] Preferably, the relationship between the depth L1 of the outer section air intake port and the depth L2 of the inner section air intake port is: 0.3≤L2 / L1≤1.

[0012] Preferably, the tubular inner wall of the inner section air intake port is tangent to the plane where the first side of the air intake port air intake pressure plate is located.

[0013] Preferably, the distance between the axis of the inner section air intake port and the bottom surface of the rear shell is W, (D2 / 2) mm≤W≤(D2 / 2+3) mm.

[0014] Preferably, the first end of the inner section air intake port is connected to the outer section air intake port, and in the vertical direction perpendicular to the plane where the air inlet air intake pressure plate is located, the second end of the inner section air intake port extends in a direction close to the second cavity.

[0015] Preferably, the first end of the inner section air intake port is connected to the outer section air intake port, and based on the plane direction of the air inlet air intake pressure plate, the second end of the inner section air intake port extends toward the projection area of ​​the power circuit module on the first side of the air inlet air intake pressure plate.

[0016] Preferably, an oblique transition is provided at the outer section air intake port and the portion connected to the inner section air intake port, and the value range of the angle α of the oblique transition is 105°≤∠α≤165°.

[0017] Preferably, the refrigerant flow rate through the inner section air intake port is greater than the refrigerant flow rate through the outer section air intake port.

[0018] An embodiment of the present invention further provides a new energy vehicle, comprising the above-mentioned horizontal compressor.

[0019] The horizontal compressor and the new energy vehicle of the present invention can accelerate the flow rate of the refrigerant and enhance the cooling effect on the power circuit module and improve the efficiency of the compressor through the stepped variable diameter structure of the air intake port without adding additional parts. BRIEF DESCRIPTION OF THE DRAWINGS

[0020] Other features, objectives and advantages of the present invention will become more apparent from a reading of the detailed description of non-limiting embodiments made with reference to the following accompanying drawings.

[0021] Figure 1 It is a cross-sectional view of a horizontal compressor according to an embodiment of the present invention.

[0022] Figure 2 yes Figure 1 A partial enlarged view of the .

[0023] Figure 3 yes Figure 1 Sectional view along AA direction.

[0024] Figure 4 It is a partial enlarged view of a horizontal compressor according to another embodiment of the present invention.

[0025] Reference numerals

[0026] 1 Middle shell

[0027] 2 Air inlet suction pressure plate

[0028] 21 External air intake

[0029] 22 Inner air intake

[0030] 3 Back cover

[0031] 4 Second cavity

[0032] 5. First cavity

[0033] D1 Diameter of the outer air inlet

[0034] D2 Inner section air inlet diameter

[0035] L1 Outer section air inlet depth

[0036] L2 Inner section suction port depth

[0037] E1 Outer section air inlet axis

[0038] E2 Inner section air inlet axis DETAILED DESCRIPTION

[0039] The following describes the implementation methods of the present application through specific examples, and those skilled in the art can easily understand other advantages and effects of the present application from the content disclosed in the present application. The present application can also be implemented or applied through other different specific implementation methods, and the details in the present application can also be modified or changed in various ways according to different viewpoints and application systems without departing from the spirit of the present application. It should be noted that the embodiments in the present application and the features in the embodiments can be combined with each other without conflict.

[0040] The following is a detailed description of the embodiments of the present application with reference to the accompanying drawings so that those skilled in the art can easily implement the present application. The present application can be embodied in a variety of different forms and is not limited to the embodiments described herein.

[0041] In the representations of the present application, the representations with reference to the terms "one embodiment", "some embodiments", "examples", "specific examples", or "some examples" etc. mean that the specific features, structures, materials or characteristics represented in conjunction with the embodiment or example are included in at least one embodiment or example of the present application. Moreover, the represented specific features, structures, materials or characteristics may be combined in any one or more embodiments or examples in a suitable manner. In addition, those skilled in the art may combine and combine the different embodiments or examples represented in the present application and the features of the different embodiments or examples, unless they contradict each other.

[0042] In addition, the terms "first" and "second" are used for descriptive purposes only and should not be understood as indicating or implying relative importance or implicitly indicating the number of technical features indicated. Therefore, a feature defined as "first" or "second" may explicitly or implicitly include at least one of the features. In the representation of this application, the meaning of "plurality" is two or more, unless otherwise clearly and specifically defined.

[0043] In order to clearly describe the present application, components irrelevant to the description are omitted, and the same reference symbols are given to the same or similar components throughout the specification.

[0044] Throughout the specification, when a device is said to be "connected" to another device, this includes not only the case of "direct connection" but also the case of "indirect connection" by placing other elements therebetween. In addition, when a device is said to "include" a certain component, unless otherwise stated, it does not exclude other components, but means that other components may be included.

[0045] When a device is said to be "on" another device, it may be directly on the other device, but there may also be other devices between it. In contrast, when a device is said to be "directly" on another device, there are no other devices between it.

[0046] Although the terms first, second, etc. are used to represent various elements in some examples, these elements should not be limited by these terms. These terms are only used to distinguish one element from another element. For example, the first interface and the second interface, etc. are represented. Moreover, as used in this article, the singular forms "one", "one" and "the" are intended to also include plural forms, unless there is an opposite indication in the context. It should be further understood that the terms "comprising" and "including" indicate the existence of features, steps, operations, elements, components, projects, kinds, and / or groups, but do not exclude the existence, occurrence or addition of one or more other features, steps, operations, elements, components, projects, kinds, and / or groups. The terms "or" and "and / or" used herein are interpreted as inclusive, or mean any one or any combination. Therefore, "A, B or C" or "A, B and / or C" means "any of the following: A; B; C; A and B; A and C; B and C; A, B and C". Only when the combination of elements, functions, steps or operations is inherently mutually exclusive in some way, will there be an exception to this definition.

[0047] The technical terms used herein are only used to refer to specific embodiments and are not intended to limit the present application. The singular form used herein also includes the plural form unless the sentence clearly indicates the contrary meaning. The meaning of "including" used in the specification is to specify specific characteristics, regions, integers, steps, operations, elements and / or components, and does not exclude the existence or addition of other characteristics, regions, integers, steps, operations, elements and / or components.

[0048] Although not defined differently, all terms, including technical and scientific terms used herein, have the same meaning as those generally understood by those skilled in the art to which this application belongs. Terms defined in commonly used dictionaries are additionally interpreted as having meanings consistent with the relevant technical literature and the contents of the current disclosure, and unless defined, shall not be overly interpreted as ideal or very formal meanings.

[0049] Figure 1 It is a cross-sectional view of a horizontal compressor according to an embodiment of the present invention. Figure 2 yes Figure 1 A partial enlarged view of the . Figure 3 yes Figure 1 The cross-sectional view along the AA axis. Figures 1 to 3As shown, a horizontal compressor of the present invention comprises: a middle shell 1 and a front shell enclosed together to form a first cavity 5, an air inlet suction plate 2 and a rear shell 3. The first cavity 5 contains a motor, a movable scroll and a fixed scroll. The air inlet suction plate 2 is arranged on the side of the motor away from the movable scroll and docked with the middle shell 1. The first side of the air inlet suction plate 2 is provided with an annular flange protruding from the middle shell 1, and an inward step-type suction hole passing through the annular flange is provided. The inward step-type suction hole includes an outer section suction port 21 that is interconnected and an inner section suction port 22 whose diameter is smaller than the outer section suction port 21. The rear shell 3 and the second side of the air inlet suction plate 2 enclose together to form a second cavity 4 for accommodating a power circuit module. The axis of the outer section suction port 21 and the axis of the inner section suction port 22 are not colinear. The inner section suction port 22 guides the refrigerant entering from the outer section suction port 21 to at least move in a direction close to the second cavity 4 during the flow process. The horizontal compressor and the new energy vehicle of the present invention can accelerate the flow rate of the refrigerant and enhance the cooling effect on the power circuit module and improve the efficiency of the compressor through the stepped variable diameter structure of the air intake port without adding additional parts.

[0050] In a preferred embodiment, continue to refer to Figure 2 The relationship between the diameter D1 of the outer air intake port 21 and the diameter D2 of the inner air intake port 22 is: 0.53≤D2 / D1≤0.68, but this is not used as an example.

[0051] In a preferred embodiment, the relationship between the depth L1 of the outer section air intake port 21 and the depth L2 of the inner section air intake port 22 is: 0.3≤L2 / L1≤1, so that the refrigerant flows through the air intake pressure plate and enters a throttling section, so that the refrigerant flow rate is increased and the cooling effect on the IPM is enhanced, but this is not used as an example.

[0052] In a preferred embodiment, the tubular inner wall of the inner section air suction port 22 is tangent to the plane where the first side of the air inlet air suction pressure plate 2 is located, but this is not an example.

[0053] In a preferred embodiment, the axis E1 of the outer air intake port 21 penetrates the annular flange along the thickness direction of the annular flange. The axis E1 of the outer air intake port 21 and the axis E2 of the inner air intake port 22 can be parallel or inclined, but this is not an example.

[0054] In a preferred embodiment, the distance from the axis E2 of the inner section air intake port 22 to the bottom surface of the rear shell is W, (D2 / 2)mm≤W≤(D2 / 2+3)mm, so as to guide the air intake flow toward the IPM and enhance the cooling effect on the IPM, but this is not used as an example.

[0055] In a preferred embodiment, the first end of the inner air inlet 22 is connected to the outer air inlet 21, and the second end of the inner air inlet 22 extends toward the projection area of ​​the first side of the air inlet pressure plate 2 close to the power circuit module based on the plane direction of the air inlet pressure plate 2. This is equivalent to tilting the inner air inlet 22 around the Z axis toward the bottom surface of the rear shell, and guiding the air flow to the IPM (IPM stands for Intelligent Power Module, which is the abbreviation of Intelligent Power Module) location area, but this is not used as an example.

[0056] In a preferred embodiment, see Figure 1 An angle transition is provided between the outer air intake port 21 and the inner air intake port 22, and the value range of the angle α of the angle transition is 105°≤∠α≤165°, but this is not taken as an example.

[0057] In a preferred embodiment, the refrigerant flow rate through the inner section air intake port 22 is greater than the refrigerant flow rate through the outer section air intake port 21 , but this is not an example.

[0058] The stepped variable diameter structure of the air intake port of the present invention increases the refrigerant flow rate and enhances the cooling effect on the IPM; the eccentric design of the inner air intake port 22 (small diameter flow channel) makes the flow channel close to the bottom surface of the rear shell, thereby enhancing the cooling effect on the IPM; the inner air intake port 22 is designed at an inclined angle relative to the outer air intake port 21 (large diameter flow channel), so that the flow channel is directed to the area where the IPM is located, thereby enhancing the cooling effect on the IPM; compared with the air intake port structure without a stepped structure, the bottom surface of the rear shell can be closer to the compressor pump body, which can enhance the cooling effect on the controller components and increase the design space of the controller structure.

[0059] The following is in conjunction with the instruction manual Figures 1 to 3 To introduce the specific implementation of the horizontal compressor of the present invention:

[0060] See also Figures 1 to 3As shown, in the horizontal compressor of the present invention, the middle shell 1 and the front shell are enclosed to form a first cavity 5, an air inlet suction plate 2 and a rear shell 3. The first cavity 5 contains a motor, a movable scroll and a fixed scroll. The air inlet suction plate 2 is arranged on the side of the motor away from the movable scroll and docked with the middle shell 1. The first side of the air inlet suction plate 2 is provided with an annular flange protruding from the middle shell 1, and an inward step-type suction hole passing through the annular flange is provided. The inward step-type suction hole includes an outer section suction port 21 that is interconnected and an inner section suction port 22 whose diameter is smaller than the outer section suction port 21. The rear shell 3 and the second side of the air inlet suction plate 2 are enclosed to form a second cavity 4 for accommodating a power circuit module. The axis of the outer section suction port 21 and the axis of the inner section suction port 22 are not colinear. The inner section suction port 22 guides the refrigerant entering from the outer section suction port 21 to at least move in a direction close to the second cavity 4 during the flow process. The relationship between the diameter D1 of the outer section air intake port 21 and the diameter D2 of the inner section air intake port 22 is: 0.53≤D2 / D1≤0.68. The relationship between the depth L1 of the outer section air intake port 21 and the depth L2 of the inner section air intake port 22 is: 0.3≤L2 / L1≤1. The tubular inner wall of the inner section air intake port 22 is tangent to the plane where the first side of the air inlet air intake pressure plate 2 is located, and the distance from the axis E2 of the inner section air intake port 22 to the bottom surface of the rear shell is W, (D2 / 2)mm≤W≤(D2 / 2+3)mm, so as to guide the air flow to the IPM and enhance the cooling effect on the IPM. The first end of the inner section air intake port 22 is connected to the outer section air intake port 21, and the second end of the inner section air intake port 22 extends to the projection area of ​​the first side of the air inlet air intake pressure plate 2 close to the power circuit module. An oblique transition is provided at the outer section air intake port 21 and the inner section air intake port 22, and the value range of the angle α of the oblique transition is 105°≤∠α≤165°, but this is not used as an example. The refrigerant flow rate through the inner section air intake port 22 is greater than the refrigerant flow rate through the outer section air intake port 21. The present invention designs the compressor air intake port as a two-stage variable diameter structure, the first section is to match the pipe diameter of the air-conditioning system, and the second section is a guide and acceleration channel for the refrigerant intake airflow. Through this structural scheme, the compressor intake airflow is enhanced with an accelerated throttling process after passing through the air intake port, the refrigerant flow rate is increased, and the cooling effect on the controller is increased. Compared with the ordinary air intake port, the bottom surface of the rear shell can be closer to the compressor pump body side when the position of the air intake port of the compressor and the whole vehicle remains unchanged, and the axial space for the arrangement of the control panel components can be more.

[0061] Figure 4 FIG. 2 is a partial enlarged view of a horizontal compressor according to another embodiment of the present invention. Figure 4As shown, another horizontal compressor of the present invention is different from the previous horizontal compressor in that the first end of the inner section air intake port 22 is connected to the outer section air intake port 21, and in the vertical direction perpendicular to the plane where the air inlet air intake pressure plate 2 is located, the second end of the inner section air intake port 22 extends in the direction close to the second cavity 4. It is equivalent to the inner section air intake port 22 deflecting the air intake port around the X-axis toward the IPM module area, and guiding the air flow direction of the air intake to the area where the IPM is located, but this is not used as an example.

[0062] According to actual needs, the first end of the inner air intake port 22 can also be set to be connected to the outer air intake port 21, and in the vertical direction perpendicular to the plane where the air inlet air intake pressure plate 2 is located, the second end of the inner air intake port 22 extends toward the direction close to the second cavity 4, and in the plane direction based on the air inlet air intake pressure plate 2, the second end of the inner air intake port 22 also extends toward the projection area of ​​the power circuit module on the first side of the air inlet air intake pressure plate 2, but this is not used as an example.

[0063] The present invention also provides a new energy vehicle, which adopts the above-mentioned horizontal compressor. The other relevant technical features and technical effects are as described above and will not be repeated here. The present invention helps to improve the whole machine NVH (Noise, Vibration, Harshness, which is a comprehensive issue to measure the quality of automobile manufacturing and is the most direct and superficial feeling for automobile users) of new energy vehicles.

[0064] In summary, the horizontal compressor and new energy vehicle of the present invention can accelerate the refrigerant flow rate, enhance the cooling effect on the power circuit module, and improve the compressor efficiency through the stepped variable diameter structure of the air intake port without adding additional parts.

[0065] The above contents are further detailed descriptions of the present invention in combination with specific preferred embodiments, and it cannot be determined that the specific implementation of the present invention is limited to these descriptions. For ordinary technicians in the technical field to which the present invention belongs, several simple deductions or substitutions can be made without departing from the concept of the present invention, which should be regarded as falling within the protection scope of the present invention.

Claims

1. A horizontal compressor, characterized in that: include: The middle shell (1) and the front shell together form a first cavity (5) for accommodating the motor, the movable scroll, and the stationary scroll; An air inlet suction pressure plate (2) is arranged on a side of the motor away from the movable scroll and docked with the middle shell (1); a first side of the air inlet suction pressure plate (2) is provided with an annular flange protruding from the middle shell (1); an inwardly contracted step-type air inlet hole is provided passing through the annular flange; the inwardly contracted step-type air inlet hole comprises an outer section air inlet (21) which is interconnected and an inner section air inlet (22) which has a diameter smaller than that of the outer section air inlet (21); The rear shell (3) and the second side of the air inlet suction pressure plate (2) together form a second cavity (4) for accommodating the power circuit module. The axis of the outer air inlet (21) and the axis of the inner air inlet (22) are not colinear. The inner air inlet (22) guides the refrigerant entering from the outer air inlet (21) to at least move in a direction close to the second cavity (4) during the flow process.

2. The horizontal compressor according to claim 1, characterized in that: The relationship between the diameter D1 of the outer section air intake port (21) and the diameter D2 of the inner section air intake port (22) is: 0.53≤D2 / D1≤0.

68.

3. The horizontal compressor according to claim 2, characterized in that: The relationship between the depth L1 of the outer section air intake port (21) and the depth L2 of the inner section air intake port (22) is: 0.3≤L2 / L1≤1.

4. The horizontal compressor according to claim 3, characterized in that: The tubular inner wall of the inner section air intake port (22) is tangent to the plane where the first side of the air intake port air intake pressure plate (2) is located.

5. The horizontal compressor according to claim 4, characterized in that: The distance between the axis (E2) of the inner section air intake port (22) and the bottom surface of the rear shell is W, (D2 / 2) mm≤W≤(D2 / 2+3) mm.

6. The horizontal compressor according to claim 1, characterized in that: The first end of the inner section air intake port (22) is connected to the outer section air intake port (21), and in a vertical direction perpendicular to the plane where the air intake pressure plate (2) is located, the second end of the inner section air intake port (22) extends in a direction close to the second cavity (4).

7. The horizontal compressor according to claim 1, characterized in that: The first end of the inner section air intake port (22) is connected to the outer section air intake port (21), and based on the plane direction of the air intake port air intake pressure plate (2), the second end of the inner section air intake port (22) extends toward a projection area close to the power circuit module on the first side of the air intake port air intake pressure plate (2).

8. The horizontal compressor according to claim 1, characterized in that: An oblique transition is provided between the outer section air intake port (21) and the portion connected to the inner section air intake port (22), and the value range of the angle α of the oblique transition is 105°≤∠α≤165°.

9. The horizontal compressor according to claim 1, characterized in that: The flow rate of the refrigerant passing through the inner section air intake port (22) is greater than the flow rate of the refrigerant passing through the outer section air intake port (21).

10. A horizontal compressor, characterized in that: Comprising the horizontal compressor as claimed in claim 1.

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