Air-supplementing enthalpy-increasing compressor and air conditioner

Abstract

The present invention provides an air-injection and heat-increasing compressor and an air conditioner. The air-injection and heat-increasing compressor includes: a cylinder, a partition or flange, and a valve body. The partition or flange has an air-injection and heat-increasing channel formed inside. The cylinder has an injection channel formed in a recessed manner. The radial inner side of the injection channel is connected to the internal cavity of the cylinder. A valve slot is also formed on the surface of the injection channel away from the partition or flange. At least part of the structure of the valve body is disposed in the valve slot. A pressure introduction slot is also provided on the side of the valve slot away from the injection channel. One end of the pressure introduction slot is connected to the valve slot, and the other end can be connected to the internal cavity of the cylinder. The valve body can move within the valve slot and the injection channel to open or close the injection channel. The hardness value H of the valve body and the hardness value H1 of the partition or flange satisfy H1 / H∈(0.2, 2). According to the present invention, the problem of poor enthalpy increase effect caused by unreasonable enthalpy increase time can be solved. The air-injection volume can also be increased while reducing the wear of the valve body and the partition or flange.

Description

Technical Field

[0001] The present invention relates to the technical field of compressors, and in particular to an air-supplementing and enthalpy-increasing compressor and an air conditioner. Background Art

[0002] Rolling rotor compressors, with their outstanding advantages of small size and simple structure, are widely used in residential and commercial air conditioners, low-temperature heat pumps, and other fields. The enthalpy-increasing channel incorporated into the pump body injects medium-pressure gas into the compression chamber, increasing cooling capacity (or heating capacity) and reducing compressor exhaust issues, further expanding the compressor's application range.

[0003] Existing enthalpy-increasing structures typically create enthalpy-increasing channels in specific areas of a partition or flange, depending on the compressor's application. This utilizes a roller-overlapping seal to address backflow when the compression chamber pressure exceeds the enthalpy-increasing pressure, as described in patent CN117287395A. This patented structure is only adaptable to specific operating conditions (selected during design). This is because when the compressor's operating conditions deviate from these specific conditions, the enthalpy-increasing ports may close prematurely or late, resulting in a poor enthalpy-increasing effect.

[0004] The prior art patent CN201351610Y discloses a roller cavity on the cylinder, in which a ball is arranged, one end of the ball is connected to the air supply channel, and the other end is connected to the cylinder cavity, and the air supply channel is opened and closed by the movement of the ball. However, since the ball is arranged in the air supply channel and the other end of the ball is connected to the cylinder air supply inlet, the pressure introduced through the cylinder air supply inlet is compared with the air supply pressure, thereby driving the ball to move to open or close the air supply channel. However, the method of introducing pressure through the cylinder air supply inlet results in a smaller cross-sectional area of ​​the air intake channel due to the obstruction of the ball, resulting in the air supply volume not meeting the required requirements. The use of the ball for air supply still results in a large leakage gap between the ball and the inner wall of the channel, resulting in the failure to meet the air supply requirements (insufficient air supply pressure or cylinder return air, etc.), and the ball will not move along the direction of the central axis during movement, and will deviate, thereby hitting the inner wall or lower end of the channel, etc., resulting in stress concentration, generating a large amount of energy consumption, resulting in reduced air supply performance and reduced air supply reliability. Similarly, the prior art patent CN202117924 U also has a method of introducing pressure through the cylinder air supply inlet, resulting in a small air supply volume and failing to meet the required requirements.

[0005] Since the valve body structure of the air-supplementing and reheat-increasing compressor in the prior art is arranged in the air-supplementing channel and the pressure is introduced through the cylinder air-supplementing inlet, resulting in a small air-supplementing volume and failing to meet the required requirements, the present invention studies and designs an air-supplementing and reheat-increasing compressor and air conditioner. Summary of the Invention

[0006] Therefore, the technical problem to be solved by the present invention is to overcome the defect in the prior art that the valve body structure of the air-supplementing and reheat-increasing compressor is arranged in the air-supplementing channel and the pressure is introduced through the cylinder air-supplementing inlet, resulting in a small air-supplementing volume and failing to meet the required requirements, thereby providing an air-supplementing and reheat-increasing compressor and air conditioner.

[0007] In order to solve the above problems, the present invention provides an air-supplementing and enthalpy-increasing compressor, which comprises:

[0008] A cylinder, a partition or flange, and a valve body, wherein the partition or flange is connected to one axial end face of the cylinder, and an air-supplementing enthalpy-increasing channel is provided inside the partition or flange, and an injection channel is provided in a recessed manner on one axial end face of the cylinder connected to the partition or flange, or an injection channel is provided in a recessed manner on one axial end face of the partition or flange connected to the cylinder;

[0009] A valve groove is also provided on the cylinder at a position connected to the injection channel, and the radial inner side of the injection channel is connected to the internal cavity of the cylinder. At least part of the structure of the valve body is arranged in the valve groove, and a pressure introduction groove is also provided on the side of the valve groove away from the injection channel. One end of the pressure introduction groove is connected to the valve groove, and the other end can be connected to the internal cavity of the cylinder. The valve body can move in the valve groove and the injection channel to open or close the injection channel; the surface hardness value of the valve body is H, the surface hardness value of the partition or flange is H1, and B=H1 / H∈(0.2, 2).

[0010] In some embodiments,

[0011] It also includes a roller, which is arranged in the cylinder. The partition or flange is made of modulated steel material, and its hardness value H1 meets: 23HRC≤H1≤60HRC. The material of the roller is gray cast iron, and the hardness value is 18-20HRC.

[0012] In some embodiments,

[0013] The pressure introduction groove can introduce the refrigerant in the internal cavity of the cylinder and act on one end of the valve body, and the air-supply and enthalpy-increasing channel can introduce the refrigerant and act on the other end of the valve body. When the refrigerant pressure introduced by the pressure introduction groove is less than the refrigerant pressure in the air-supply and enthalpy-increasing channel, the valve body moves toward the direction of the pressure introduction groove and opens the injection channel. When the refrigerant pressure introduced by the pressure introduction groove is greater than the refrigerant pressure in the air-supply and enthalpy-increasing channel, the valve body moves toward the injection channel and closes the injection channel. When the injection channel is opened, the refrigerant in the air-supply and enthalpy-increasing channel can be replenished into the internal cavity of the cylinder through the injection channel.

[0014] In some embodiments,

[0015] An exhaust bevel is provided on the axial end face of the cylinder away from the partition or flange, and the radial inner side of the exhaust bevel is connected to the internal cavity of the cylinder. One end of the pressure introduction groove extends to connect with the exhaust bevel to communicate with the internal cavity, so as to introduce the refrigerant in the internal cavity into the pressure introduction groove.

[0016] In some embodiments,

[0017] The pressure introduction groove extends along the axial direction of the cylinder, the air-supplementing enthalpy-increasing channel extends along the radial direction of the cylinder, and an enthalpy-increasing port is also provided on the partition or flange. The enthalpy-increasing port extends from one axial end face of the partition or flange toward the interior of the partition or flange, extending to communicate with the air-supplementing enthalpy-increasing channel, and the enthalpy-increasing port is connected to the injection channel.

[0018] In some embodiments,

[0019] In the projection surface of the longitudinal plane, in the axial direction perpendicular to the cylinder, the width of the pressure introduction groove is smaller than the width of the valve groove, the width of the valve groove is smaller than the width of the injection channel, and the width of the valve body in the axial direction perpendicular to the cylinder is smaller than the width of the valve groove in this direction, so that a clearance fit is formed between the valve body and the valve groove.

[0020] In some embodiments,

[0021] One end face of the valve body facing the partition or flange is the first end face, and the axial end face of the partition or flange facing the cylinder is the second end face, wherein the maximum distance between the first end face and the second end face is the stroke L of the valve body, and L is set to: 0.05mm≤L≤1.5mm.

[0022] In some embodiments,

[0023] The valve body is a cylindrical structure, and the valve groove, the pressure introduction groove and the injection channel are also cylindrical structures. One end face of the valve body facing the partition or flange is a plane, and one end face of the valve body facing the pressure introduction groove is also a plane. In the projection surface of the longitudinal plane, the valve body is a rectangular structure, and the valve groove, the pressure introduction groove and the injection channel are also rectangular structures.

[0024] In some embodiments,

[0025] 0.01mm≤λ≤0.1mm;

[0026] Wherein, λ is the gap between the valve slot and the valve body in a direction perpendicular to the central axis of the valve slot, that is, valve slot diameter minus valve body diameter.

[0027] In some embodiments,

[0028] d is the diameter of the valve body, 4mm≤d<12mm.

[0029] In some embodiments,

[0030] h is the length of the valve body along its central axis, that is, the thickness of the valve body, 1mm≤h<3mm.

[0031] In some embodiments,

[0032] ρ is the valve body density, ρ<5000kg / m^3.

[0033] In some embodiments,

[0034] L is the valve body stroke, L≤0.6mm.

[0035] In some embodiments,

[0036] One end face of the valve body facing the partition or flange is the first end face, and one end face of the cylinder facing the partition or flange is the third end face, wherein the minimum distance between the first end face and the third end face is h0, h is the length of the valve body on its central axis, and: h0 / h<0.5.

[0037] In some embodiments,

[0038] The air-compensating and reheat-increasing compressor is a two-cylinder compressor, wherein the cylinder comprises an upper cylinder and a lower cylinder, the partition plate or flange is a partition plate disposed between the upper cylinder and the lower cylinder, the upper cylinder is provided with a pressure introduction groove 1, a valve groove 1, and an injection channel 1, the valve body comprises a valve body 1 and a valve body 2, at least a portion of the structure of the valve body 1 is disposed in the valve groove 1, and at least a portion of the structure of the valve body 1 is disposed in the injection channel 1, and the valve body 1 can move in the valve groove 1 and the injection channel 1 to open or close the injection channel 1;

[0039] The lower cylinder is provided with a second pressure introduction groove, a second valve groove and a second injection channel. At least a portion of the structure of the second valve body is disposed in the second valve groove, and at least a portion of the structure of the second valve body is disposed in the second injection channel. The second valve body can move in the second valve groove and the second injection channel to open or close the second injection channel.

[0040] The enthalpy increase port includes enthalpy increase port 1 and enthalpy increase port 2. The enthalpy increase port 1 is opened from the axial end surface of the partition facing the upper cylinder in the direction toward the interior of the partition, and is connected to the air-supplementing enthalpy increase channel. The enthalpy increase port 2 is opened from the axial end surface of the partition facing the lower cylinder in the direction toward the interior of the partition, and is connected to the air-supplementing enthalpy increase channel.

[0041] In some embodiments,

[0042] The air-compensating and reheat-increasing compressor is a single-cylinder compressor, the partition or flange includes an upper flange and a lower flange, the cylinder is provided with the pressure introduction groove, the valve groove and the injection channel, at least part of the structure of the valve body is provided in the valve groove, at least part of the structure of the valve body is provided in the injection channel, and the valve body can move in the valve groove and the injection channel to open or close the injection channel;

[0043] The enthalpy increase port and the air-compensating enthalpy increase channel are disposed on the upper flange or the lower flange. The enthalpy increase port extends from an axial end surface of the upper flange or the lower flange facing the cylinder, in an inward direction of the upper flange or the lower flange, to communicate with the air-compensating enthalpy increase channel. The present invention also provides an air conditioner comprising the aforementioned air-compensating enthalpy increase compressor.

[0044] The air-injection enthalpy-increasing compressor and air conditioner provided by the present invention have the following beneficial effects:

[0045] 1. The present invention provides an air-supply and enthalpy-increasing channel on a partition or flange, and an injection channel is provided on the end surface of the cylinder facing the partition or flange, or the injection channel is provided on the end surface of the partition or flange facing the cylinder, a valve slot is provided on the cylinder in contact with the injection channel, and a pressure introduction slot is provided on the other side of the valve slot, which can introduce the refrigerant in the internal cavity of the cylinder, and at least part of the structure of the valve body is provided in the valve slot, so that one end of the valve body can withstand the refrigerant pressure in the cylinder introduced from the pressure introduction slot, and the other end of the valve body can withstand the air-supply pressure from the air-supply and enthalpy-increasing channel, so that the valve body can be driven to open or close the injection channel according to the relationship between the air-supply pressure and the pressure in the internal cavity of the cylinder, the injection channel is opened when the air-supply pressure is greater than the internal cavity pressure, and the injection channel is closed when the air-supply pressure is less than the internal cavity pressure of the cylinder, so as to realize the air-supply and cylinder pressure control. The relationship automatically controls the effect of whether to replenish air, improves the timeliness of opening or closing of the check valve, can adaptively adjust the time of replenishing air according to the size of the working conditions, and solves the problem of poor enthalpy increase effect caused by unreasonable enthalpy increase time; and the present invention also introduces the pressure into the groove. Compared with the existing method of introducing refrigerant pressure through the cylinder replenishing inlet, the injection channel can be fully opened without forming an obstruction thereto, and the replenishing air volume can be effectively increased to meet the required replenishing air requirements; and the present invention sets the ratio of the hardness value of the valve body and the hardness value of the partition or flange at B=H1 / H∈(0.2, 2), which can effectively reduce the wear of the valve body and the wear of the partition or flange; and the present invention sets the hardness value of the partition or flange at 23HRC≤H1≤60HRC, which can further reduce the wear of the partition or flange.

[0046] 2. Since the present invention is provided with a pressure introduction groove, there is no need to set the channel cross-sectional area of ​​the valve groove to be larger, but the flow area of ​​the valve groove can be reduced. It is only necessary to ensure that the valve body can move in it, thereby effectively avoiding the valve body from tilting and deviating from the central axis during movement, ensuring that it always moves up and down along the central axis, preventing it from hitting the inner wall of the valve groove, and increasing the contact surface between the valve body and the partition (forming surface contact, avoiding point contact caused by tilt, etc.), reducing stress concentration, thereby reducing wear on the partition, reducing energy consumption, and improving operational reliability; and in addition to serving as the compression chamber pressure introduction channel on the back of the valve body, the pressure introduction groove of the present invention can also serve as a resonance chamber of the compressor, which can effectively reduce the airflow noise of the compressor.

[0047] 3. The present invention also achieves a better enthalpy increase effect and reduces the compressor noise caused by the impact of the valve on the partition by setting the stroke L of the valve body to meet 0.05mm≤L≤1.5mm. The present invention further sets the inclination angle α of the valve body to meet:

[0048] The angles α≤5°, 0.01mm≤λ≤0.1mm can effectively reduce the collision between the valve body and the inner wall of the valve slot and the end face of the partition, reduce stress concentration, reduce and prevent severe wear of the partition, significantly improve the wear problem of the partition and significantly improve the reliability of the compressor;

[0049] 4. The present invention further sets the momentum I of the valve body when colliding with the partition or flange to satisfy:

[0050] And I < 0.01kg·m / s; it can effectively ensure that the valve body can move smoothly in the valve groove, reduce the collision between the valve body and the inner wall of the valve groove and the partition, reduce stress, and further improve the wear problem of the partition, thereby further improving the reliability of the compressor. BRIEF DESCRIPTION OF THE DRAWINGS

[0051] Figure 1 It is a partial cross-sectional view of the air-increasing enthalpy-increasing channel portion of the air-increasing enthalpy-increasing compressor of the present invention;

[0052] Figure 1a is a partial cross-sectional view of the air-supplementing and enthalpy-increasing passage portion of the air-supplementing and enthalpy-increasing compressor according to an alternative embodiment of the present invention;

[0053] Figure 2 yes Figure 1 A partial enlarged view of part B (preferably a double cylinder);

[0054] Figure 2a yes Figure 1a A partial enlarged view of part B' (preferably a double cylinder);

[0055] Figure 3 This is a top view of the cylinder + roller + valve body of the air-injection and enthalpy-increasing compressor of the present invention;

[0056] Figure 4 1. It is a top view of the cylinder of the air-compensating and enthalpy-increasing compressor of the present invention;

[0057] Figure 5 yes Figure 4 The cross-sectional view of the AA surface;

[0058] Figure 6 is a graph showing the relationship between enthalpy increase, noise and valve body stroke of the present invention;

[0059] Figure 7 yes Figure 2 A partial cross-sectional view of the valve body when tilted;

[0060] Figure 8 is a graph showing the relationship between the gap λ and the inclination angle α of the present invention;

[0061] Figure 9 is a graph showing the relationship between the force F between the valve body and the partition and the collision momentum I of the present invention;

[0062] Figure 10 is a graph showing the relationship between the density of the valve body material and the amount of valve body wear of the present invention;

[0063] Figure 11 is a graph showing the relationship between the material hardness of the partition or flange of the present invention and the amount of wear of the partition or flange;

[0064] Figure 12 It is a partial enlarged view of the cylinder of the present invention when it is a single cylinder.

[0065] The reference numerals indicate:

[0066] 1. Cylinder; 11. Upper cylinder; 12. Lower cylinder; 2. Partition or flange; 21. Upper flange; 22. Lower flange; 3. Valve body; 31. Valve body 1; 32. Valve body 2; 4. Air supply enthalpy increase channel; 5. Injection channel; 51. Injection channel 1; 52. Injection channel 2; 6. Valve slot; 61. Valve slot 1; 62. Valve slot 2; 63. First side of valve slot; 64. Second side of valve slot; 65. Valve slot wall; 7. Pressure introduction slot; 71. Pressure introduction slot 1; 72. Pressure introduction slot 2; 8. Enthalpy increase port; 81. Enthalpy increase port 1; 82. Enthalpy increase port 2; 9. Exhaust bevel; 10. Liquid distributor; 13. Enthalpy increase component; 14. Eccentric part of crankshaft; 15. Roller; 16. Compression chamber; 17. Sliding vane. DETAILED DESCRIPTION

[0067] The following will be combined with the accompanying drawings in the embodiments of the present invention to clearly and completely describe the technical solutions in the embodiments of the present invention. Obviously, the embodiments described are only part of the embodiments of the present invention, rather than all the embodiments. The following description of at least one exemplary embodiment is actually only illustrative and is in no way intended to limit the present invention and its application or use. Based on the embodiments of the present invention, all other embodiments obtained by ordinary technicians in this field without making creative efforts are within the scope of protection of the present invention.

[0068] It should be noted that the terms used herein are only for describing specific embodiments and are not intended to limit the exemplary embodiments according to the present application. As used herein, unless the context clearly indicates otherwise, the singular form is also intended to include the plural form. In addition, it should be understood that when the terms "comprise" and / or "include" are used in this specification, they indicate the presence of features, steps, operations, devices, components and / or combinations thereof.

[0069] Unless otherwise specifically stated, the relative arrangement of the parts and steps, the numerical expressions and the numerical values ​​set forth in these embodiments do not limit the scope of the present invention. At the same time, it should be understood that, for ease of description, the sizes of the various parts shown in the drawings are not drawn according to the actual proportional relationship. The techniques, methods and equipment known to those of ordinary skill in the relevant art may not be discussed in detail, but where appropriate, the techniques, methods and equipment should be considered as part of the authorization specification. In all examples shown and discussed here, any specific values ​​should be interpreted as being merely exemplary and not as limiting. Therefore, other examples of the exemplary embodiments may have different values. It should be noted that similar numbers and letters represent similar items in the following figures, and therefore, once an item is defined in one figure, it does not need to be further discussed in subsequent figures.

[0070] In the description of the present invention, it should be understood that the directions or positional relationships indicated by directional words such as "front, back, up, down, left, right", "horizontal, vertical, perpendicular, horizontal" and "top, bottom" are usually based on the directions or positional relationships shown in the accompanying drawings. They are only for the convenience of describing the present invention and simplifying the description. Unless otherwise specified, these directional words do not indicate or imply that the device or element referred to must have a specific direction or be constructed and operated in a specific direction. Therefore, they cannot be understood as limiting the scope of protection of the present invention; the directional words "inside and outside" refer to the inside and outside relative to the outline of each component itself.

[0071] For ease of description, spatially relative terms such as "above", "above", "on the upper surface of", "above", etc. may be used herein to describe the spatial positional relationship of a device or feature to other devices or features as shown in the figures. It should be understood that spatially relative terms are intended to include different orientations of the device in use or operation in addition to the orientation described in the figures. For example, if the device in the drawings is inverted, the device described as "above other devices or structures" or "above other devices or structures" will be positioned as "below other devices or structures" or "below other devices or structures". Thus, the exemplary term "above" can include both "above" and "below". The device can also be positioned in other different ways (rotated 90 degrees or in other orientations), and the spatially relative descriptions used here are interpreted accordingly.

[0072] In addition, it should be noted that the use of terms such as "first" and "second" to limit components is only for the convenience of distinguishing the corresponding components. Unless otherwise stated, the above terms have no special meaning and therefore cannot be understood as limiting the scope of protection of the present invention.

[0073] like Figure 1-12As shown, the present invention provides an air-supplementing enthalpy-increasing compressor (preferably a rolling rotor type enthalpy-increasing compressor), which includes:

[0074] Cylinder 1, partition or flange 2 and valve body 3, the partition or flange 2 is connected to the axial end face of the cylinder 1, and the interior of the partition or flange 2 is provided with a gas supplementary enthalpy increasing channel 4, and the axial end face of the cylinder 1 connected to the partition or flange 2 is provided with an injection channel 5 in a concave manner (see Figure 1 and 2 ), or the axial end surface of the partition plate or flange 2 connected to the cylinder 1 is provided with an injection channel 5 in a concave manner (see Figure 1a and 2a );

[0075] A valve slot 6 is also provided on the cylinder 1 at a position connected to the injection channel 5. The radial inner side of the injection channel 5 is connected to the internal cavity of the cylinder 1. At least part of the structure of the valve body 3 is disposed in the valve slot 6. A pressure introduction slot 7 is also provided on the side of the valve slot 6 away from the injection channel 5. One end of the pressure introduction slot 7 is connected to the valve slot 6, and the other end can be connected to the internal cavity of the cylinder 1. The valve body 3 can move in the valve slot 6 and the injection channel 5 to open or close the injection channel 5. The surface hardness is measured using a hardness tester of the same specification. The surface hardness of the valve body 3 is H, and the surface hardness of the partition or flange 2 is H1, and B = H1 / H∈(0.2, 2). Surface hardness refers to the ability of an object's surface to resist deformation or damage. It is usually measured using a hardness tester. The present invention preferably uses Rockwell hardness (HRC) for characterization.

[0076] The present invention provides an air-supplementing and heat-increasing channel on a partition or flange, and an injection channel is provided on the end surface of the cylinder facing the partition or flange, or the injection channel is provided on the end surface of the partition or flange facing the cylinder, a valve slot is provided on the cylinder in contact with the injection channel, and a pressure introduction slot is provided on the other side of the valve slot, which can introduce the refrigerant in the internal cavity of the cylinder, and at least part of the structure of the valve body is provided in the valve slot, so that one end of the valve body can withstand the refrigerant pressure in the cylinder introduced from the pressure introduction slot, and the other end of the valve body can withstand the air-supplementing pressure from the air-supplementing and heat-increasing channel, so that the air-supplementing pressure and the cylinder pressure can be adjusted according to the air-supplementing pressure and the cylinder pressure. When the pressure of the air supply is greater than that of the internal cavity, the valve body is driven to open or close the injection channel. When the air supply pressure is greater than the pressure of the internal cavity, the injection channel is opened, and when the air supply pressure is less than the pressure of the internal cavity of the cylinder, the injection channel is closed. This realizes the effect of automatically controlling whether to supply air according to the relationship between the air supply and the cylinder pressure, improves the timeliness of opening or closing the check valve, and can adaptively adjust the time of supplying air according to the size of the working condition, thereby solving the problem of poor enthalpy increase effect caused by unreasonable enthalpy increase time. In addition, the present invention also adopts the setting form of the pressure introduction groove, compared with the prior art In terms of the method of introducing refrigerant pressure through the cylinder air supply inlet, the injection channel can be fully opened without forming any obstruction thereto, and the air supply volume can be effectively increased to meet the required air supply requirements. Since the pressure introduction groove is provided in the present invention, it is not necessary to set the channel cross-sectional area of ​​the valve groove to be larger, but the flow area of ​​the valve groove can be reduced. It is only necessary to ensure that the valve body can move in it, thereby effectively avoiding the situation where the valve body tilts and deviates from the central axis during movement, ensuring that it always moves up and down along the central axis, preventing it from hitting the inner wall of the valve groove, and increasing the contact surface between the valve body and the partition (forming surface contact, avoiding point contact caused by tilting, etc.), reducing stress concentration, thereby reducing wear on the partition, reducing energy consumption, and improving operational reliability. In addition to serving as a compression chamber pressure introduction channel on the back of the valve body, the pressure introduction groove of the present invention can also serve as a resonance chamber of the compressor, which can effectively reduce the airflow noise of the compressor. In addition, the ratio of the hardness value of the valve body to the hardness value of the partition or flange is set at B=H1 / H∈(0.2, 2), which can effectively reduce the wear of the valve body and the wear of the partition or flange.

[0077] In some embodiments,

[0078] It also includes a roller 15, which is arranged in the cylinder. The partition or flange 2 is made of a tempered steel material, and its hardness value H1 satisfies: 23HRC≤H1≤60HRC, and its optimal value is 30HRC≤H1≤45HRC. First, the grinding performance is better; second, the material of the roller 15 is gray cast iron HT250, and the hardness value is 18-20HRC. The greater the difference, the more likely it is to cause roller wear;

[0079] The partition or flange 2 is manufactured by oil quenching at 850°C, tempering at 400°C, and for 120 minutes to achieve the optimal hardness H1 value.

[0080] The present invention sets the hardness of the partition or flange to 23HRC≤H1≤60HRC, which can further reduce the wear of the partition or flange. HRC in the present invention is a unit value representing Rockwell hardness: the hardness can be obtained using a 150kg load and a diamond cone indenter, and is used for very hard materials.

[0081] like Figure 11 The relationship between the hardness of the partition or flange material and the amount of wear, the valve body structure is quantitative, after verification of a variety of materials, the fitting curve of the partition material hardness and wear relationship, it can be concluded that: the higher the hardness of the partition or flange, the smaller the wear, when the hardness value of the partition or flange is greater than 24HRC, the wear trend is stable and there is basically no wear.

[0082] By optimizing material combinations and combining the momentum formula, valve density ρ is a key parameter. Materials with lower density than steel can be selected for the valve body, such as titanium alloys, aluminum alloys, and other lightweight materials. Suitable material densities ρ should be <5000kg / m^3. The surface hardness of the valve body is H, and the surface hardness of the diaphragm or flange is H1, with B = H1 / H∈(0.2, 2). The optimal ratio range is B∈(1.1, 1.6). If the valve hardness is low and the diaphragm hardness is high, the valve will be difficult to machine due to the low material hardness. Since the material hardness is proportional to the density, the valve will experience increased wear. If the valve hardness is high and the diaphragm hardness is low, according to the momentum formula, the valve momentum increases, and the diaphragm hardness is low, making it more susceptible to wear. Therefore, the diaphragm wear will be increased during the collision process.

[0083] In some embodiments,

[0084] The pressure introduction groove 7 can introduce the refrigerant in the internal cavity of the cylinder 1 and act on one end of the valve body 3, and the air-supplying and enthalpy-increasing channel 4 can introduce the refrigerant and act on the other end of the valve body 3. When the refrigerant pressure introduced by the pressure introduction groove 7 is less than the refrigerant pressure in the air-supplying and enthalpy-increasing channel 4, the valve body 3 moves toward the direction of the pressure introduction groove 7 and opens the injection channel 5. When the refrigerant pressure introduced by the pressure introduction groove 7 is greater than the refrigerant pressure in the air-supplying and enthalpy-increasing channel 4, the valve body 3 moves toward the direction of the injection channel 5 and closes the injection channel 5. When the injection channel 5 is opened, the refrigerant in the air-supplying and enthalpy-increasing channel 4 can be replenished into the internal cavity of the cylinder 1 through the injection channel 5.

[0085] This is a further preferred structural form of the pressure introduction groove of the present invention, which can introduce the refrigerant pressure of the compression chamber, and automatically control whether the valve body moves to open the injection channel for air replenishment, or close the injection channel for air replenishment according to the size relationship between the compression pressure and the air replenishment pressure. The specific time of air replenishment is adaptively adjusted according to the size of the working conditions, which solves the problem of poor enthalpy increase effect caused by unreasonable enthalpy increase time.

[0086] The compression chamber pressure introduction channel (pressure introduction groove 7) of the present invention connects to the cylinder exhaust bevel on one side and to the valve's side away from the enthalpy increase port on the other. This side of the channel is blocked by the valve. Regardless of the valve's position, this channel only serves to introduce pressure into the compression chamber and does not serve as a channel for injecting intermediate-pressure refrigerant. Furthermore, this channel has a certain amount of clearance volume, which acts as a compression chamber resonance cavity, thereby silencing the gas.

[0087] In some embodiments,

[0088] An exhaust bevel 9 is provided on the axial end face of the cylinder 1 away from the partition or flange 2, and the radial inner side of the exhaust bevel 9 is connected to the internal cavity of the cylinder 1. One end of the pressure introduction groove 7 extends to connect with the exhaust bevel 9 to communicate with the internal cavity, so that the refrigerant in the internal cavity can be introduced into the pressure introduction groove 7.

[0089] This is the preferred structural form of the present invention. The refrigerant in the internal cavity of the cylinder can be led out to the pressure introduction groove through the exhaust oblique cut opened on the axial end face of the cylinder, so as to provide the compression chamber pressure condition to one end of the pressure introduction groove, and ensure that the valve body can automatically open the valve body for air replenishment or close the air replenishment according to the size of the compression chamber pressure and the air replenishment pressure.

[0090] In some embodiments,

[0091] The pressure introduction groove 7 extends along the axial direction of the cylinder 1, and the air-supplementing enthalpy-increasing channel 4 extends along the radial direction of the cylinder 1. The partition plate or flange 2 is also provided with an enthalpy-increasing port 8. The enthalpy-increasing port 8 extends from an axial end face of the partition plate or flange 2 (preferably along the axial direction) toward the interior of the partition plate or flange 2, extending to communicate with the air-supplementing enthalpy-increasing channel 4, and the enthalpy-increasing port 8 is connected to the injection channel 5.

[0092] This is the preferred structural form of the pressure introduction groove, the air supplement enthalpy increase channel and the enthalpy increase port of the present invention, that is, the pressure introduction groove preferably extends along the axial direction of the cylinder, such as Figure 1 As shown, it preferably extends in the vertical direction, and the air supply channel preferably extends in the radial direction, as shown in FIG. Figure 1As shown, it extends in the horizontal direction. Through the setting of the enthalpy increase port, the air-supply refrigerant in the air-supply channel can be guided to the end face of the valve body through the enthalpy increase port, so that the valve body can be pushed to move according to the size of the air-supply pressure to open the injection channel, thereby realizing the functions of automatic air supply and automatic closing of air supply according to the size relationship between the air-supply pressure and the compression pressure.

[0093] In some embodiments,

[0094] In the projection surface of the longitudinal plane, in the axial direction perpendicular to the cylinder 1, the width of the pressure introduction groove 7 is smaller than the width of the valve groove 6, the width of the valve groove 6 is smaller than the width of the injection channel 5, and the width of the valve body 3 in the axial direction perpendicular to the cylinder 1 is smaller than the width of the valve groove 6 in this direction, so that a clearance fit is formed between the valve body 3 and the valve groove 6.

[0095] The pressure introduction groove of the present invention is preferably smaller than the width of the valve groove. The pressure introduction groove only needs to introduce the pressure in the compression chamber, and there is no need to open a larger channel area to avoid affecting the strength of the cylinder. The valve groove width is smaller than the width of the injection channel. The valve groove only needs to accommodate the valve body therein. Reducing the width of the valve groove can effectively limit the valve body and prevent the valve body from offsetting or tilting during movement, thereby avoiding the valve body colliding with the partition or the inner wall of the valve groove and causing stress concentration, reducing the wear of the partition, etc., and improving operational reliability; the width of the injection channel is large to ensure that there is a sufficient flow of refrigerant to replenish air and increase enthalpy in the compression chamber, thereby improving enthalpy increase performance.

[0096] In some embodiments,

[0097] One end face of the valve body 3 facing the partition or flange 2 is the first end face, and the axial end face of the partition or flange 2 facing the cylinder 1 is the second end face, wherein the maximum distance between the first end face and the second end face is the stroke L of the valve body 3, and L is set to: 0.05mm≤L≤1.5mm.

[0098] The present invention also achieves a better enthalpy increase effect by setting the stroke L of the valve body to meet 0.05mm≤L≤1.5mm, and can also reduce the compressor noise caused by the impact of the valve on the partition. Figure 6As shown. The present invention has requirements for the valve body stroke: the movement of the valve from closing the enthalpy increase port to fully opening the enthalpy increase port is called the stroke L, that is, the distance moved when one side of the valve moves from the state of contact with the first side of the cylinder valve groove to the state of contact with the partition on the other side of the valve. The size of the stroke L has an important influence on the enthalpy increase performance and noise. A smaller stroke will reduce the enthalpy increase effect, but due to the smaller stroke, the impact force of the valve on the partition is small, which can reduce the noise of the compressor; a larger stroke will improve the enthalpy increase effect, but due to the larger stroke, the impact force on the partition is larger, resulting in increased noise in the compressor. Therefore, it is necessary to strictly limit the stroke of the valve to achieve higher comprehensive performance. Through a large number of experimental studies, it was found that when the valve stroke is set at: 0.05mm≤L≤1.5mm, a better enthalpy increase effect can be obtained; further, when the valve stroke is set at 0.05mm≤L≤1mm, it can not only improve the compressor enthalpy increase effect, but also reduce the compressor noise caused by the impact of the valve on the partition.

[0099] In some embodiments,

[0100] The valve body 3 is a cylindrical structure, and the valve groove 6, the pressure introduction groove 7 and the injection channel 5 are also cylindrical structures. The end face of the valve body 3 facing the partition or flange 2 is a plane, and the end face of the valve body 3 facing the pressure introduction groove 7 is also a plane. In the projection surface of the longitudinal plane, the valve body 3 is a rectangular structure, and the valve groove 6, the pressure introduction groove 7 and the injection channel 5 are also rectangular structures.

[0101] This is the preferred structural form of the valve body, valve slot, pressure introduction slot and injection channel of the present invention, that is, they are all cylindrical structures with a rectangular longitudinal cross-section, ensuring that the upper and lower end faces of the valve body are both flat, which can increase the contact area between the valve body and the partition, reduce stress concentration, and at the same time increase the contact area between the valve body and the bottom surface of the valve slot, reducing stress concentration.

[0102] In some embodiments,

[0103] In the longitudinal section, the angle between the central axis of the valve body 3 and the central axis of the valve slot 6 is the inclination angle α of the valve body 3, and:

[0104] And α≤5°, 0.01mm≤λ≤0.1mm;

[0105] Wherein h is the length of the valve body 3 on its central axis, that is, the valve body thickness, d is the diameter of the valve body 3, and λ is the gap between the valve slot 6 and the valve body 3 in the direction perpendicular to the central axis of the valve slot 6, that is, the valve slot diameter minus the valve body diameter, that is, the valve slot diameter D minus the valve body diameter d.

[0106] The present invention further sets the inclination angle α of the valve body to satisfy:

[0107] And with α≤5°, 0.01mm≤λ≤0.1mm, it can effectively reduce the collision between the valve body and the inner wall of the valve groove and the end face of the partition, reduce stress concentration, reduce and prevent severe wear of the partition, so that the wear problem of the partition is significantly improved, and the reliability of the compressor is significantly improved (if the design is unreasonable, for example, the width of the valve groove is much larger than the width of the valve body, tilting will occur).

[0108] The reliability of the valve structure of the present invention is improved: when the enthalpy increase starts, the valve completes an opening and closing process for each rotation of the compressor. The number of times the valve is opened and closed during the entire operating cycle of the compressor will reach billions of times. When the valve is open, the valve collides with the first side of the cylinder valve slot, and when the valve is closed, the valve collides with the adjacent partition. Since the gas force on the first and second sides of the valve is uneven when the valve is opened and closed, the valve tilts when it moves in the valve slot, and the contact surface is greatly reduced when the valve collides with the partition, and the stress in the contact surface area is significantly increased. After long-term operation of the compressor, the partition will wear out, and in severe cases, the compressor will be damaged. After in-depth research and analysis and a large number of experimental verifications, it is concluded that if the inclination angle of the valve during operation can be reduced through the cylinder valve slot and the contact area of ​​the valve and the partition can be increased, the reliability of the compressor will be significantly improved. According to the geometric relationship between the valve and the cylinder valve slot, the inclination angle α (unit: °) of the valve satisfies the relationship:

[0109] Where: h is the valve thickness, d is the valve diameter, and λ is the gap between the cylinder valve slot and the valve (cylinder valve slot diameter - valve diameter).

[0110] Analyzing the relationship between the valve's tilt angle α, it was found that the greater the valve thickness h, the smaller the valve tilt angle α; the larger the valve clearance, the larger the valve tilt angle α; and the valve aperture has little effect on the valve tilt angle. Therefore, there are two effective methods to reduce the valve tilt angle α: 1. Increasing the valve thickness h; 2. Reducing the clearance λ between the valve and the cylinder valve slot. Experimental verification of reducing the clearance between the valve and the valve slot: To verify the effectiveness of the two aforementioned methods in improving compressor reliability, experiments were conducted to increase the valve thickness h and reduce the clearance λ between the valve and the cylinder valve slot. The results showed that the thicker the valve thickness h, the more severe the partition wear and the worse the compressor reliability. Simultaneously reducing the valve thickness h and the clearance λ ensured that the valve's tilt angle α was ≤5°. The partition wear problem was significantly improved, and the compressor reliability was significantly enhanced.

[0111] In some embodiments,

[0112] The momentum of the valve body 3 when colliding with the partition or flange 2 is I, and:

[0113] And I < 0.01 kg·m / s;

[0114] Wherein, h is the length of the valve body 3 on its central axis, i.e., the thickness of the valve body, d is the diameter of the valve body 3, Δp is the pressure difference between the two side end faces of the valve body 3, ρ is the valve body density, and L is the valve body stroke.

[0115] The present invention further sets the momentum I of the valve body when colliding with the partition or flange to satisfy:

[0116] And I < 0.01kg·m / s; it can effectively ensure that the valve body can move smoothly in the valve groove, reduce the collision between the valve body and the inner wall of the valve groove and the partition, reduce stress, and further improve the wear problem of the partition, thereby further improving the reliability of the compressor.

[0117] In some embodiments,

[0118] 4mm≤d<12mm, 1mm≤h<3mm, ρ<5000kg / m^3, L≤0.6mm.

[0119] Further analysis of the velocity, kinetic energy, and momentum parameters of the valve and the partition during collision revealed that the smaller the momentum of the valve and the partition during collision, the smaller the force between the valve and the partition. Analyzing the motion of the valve within the cylinder valve slot, it was found that the momentum I of the valve and the partition during collision satisfies the relationship:

[0120]

[0121] Where: d is the valve diameter, △p is the pressure difference on both sides of the valve (unit: pa), ρ is the valve density, h is the valve thickness, and L is the valve stroke.

[0122] From equation ②, we can see that increasing the valve thickness h increases the momentum I when the valve collides with the diaphragm. This explains why increasing the valve thickness h to reduce the valve tilt angle α actually leads to increased diaphragm wear. Therefore, it is necessary to limit the momentum I when the valve collides with the diaphragm while limiting the maximum valve tilt angle α.

[0123] Based on equations ① and ② and the experimental results, in order to improve the reliability of the compressor, the following two aspects need to be restricted:

[0124] 1. Valve tilt angle α limit: α≤4°, the corresponding clearance λ should be ≤0.1mm. At the same time, to ensure that the valve can move smoothly in the cylinder valve slot, the clearance λ should be ≥0.01mm, that is, 0.01mm≤λ≤0.1mm;

[0125] 2. Limiting the momentum I when the valve collides with the cylinder valve slot: To ensure compressor reliability, momentum I should be less than 0.01 kg.m / s. To further improve compressor reliability, momentum I should be less than or equal to 0.005 kg.m / s. To achieve this, reducing the momentum I can be accomplished by reducing the valve diameter d, valve density ρ, valve thickness h, and valve travel L.

[0126] Valve diameter d: Valve momentum I is proportional to the square of the valve diameter. Therefore, reducing valve diameter d can significantly reduce momentum I and improve compressor reliability. However, an excessively small valve diameter d will limit the flow area of ​​enthalpy increase port 1 81 (or enthalpy increase port 2 82) (when the valve is closed, it covers the partition enthalpy increase port 1 81 or enthalpy increase port 2 82, preventing refrigerant in the compression chamber from flowing into the enthalpy increase port. Therefore, the diameter of the partition enthalpy increase port 1 81 or enthalpy increase port 2 82 should be smaller than valve diameter d), affecting compressor performance. From a comprehensive perspective of reliability and performance, the valve diameter d range of 4mm ≤ d < 12mm can best balance compressor reliability and performance.

[0127] Valve thickness h: Excessive valve thickness h increases valve momentum I, reducing compressor reliability. Excessive valve thickness h increases the inclination angle α of the valve during movement within the valve slot, reducing compressor reliability. Experimental research has shown that the optimal valve thickness h range is 1mm ≤ h < 3mm.

[0128] Valve density ρ: Valve materials can be made of materials with lower density than steel, such as titanium alloy, aluminum alloy and other lightweight materials. The corresponding material density ρ is less than 5000kg / m^3.

[0129] Stroke L: In order to reduce the valve momentum I, the more appropriate stroke range is: L≤0.6mm.

[0130] In some embodiments,

[0131] One end face of the valve body facing the partition or flange is the first end face, and one end face of the cylinder facing the partition or flange is the third end face, wherein the minimum distance between the first end face and the third end face is h0, h is the length of the valve body on its central axis, and: h0 / h<0.5.

[0132] By limiting the ratio h0 / h to meet the above range, the present invention can ensure that the valve slot exerts sufficient constraint on the valve body, preventing the valve body from tilting too much due to insufficient constraint on the valve body, thereby preventing stress concentration from occurring.

[0133] The valve body of the present invention moves in the space (injection channel) enclosed by the valve slot and the partition (or flange). The momentum formula when the valve collides with the partition is expressed as follows: Where d is the valve diameter, △p is the pressure difference across the valve (unit: pa), ρ is the valve density, h is the valve thickness, and L is the valve stroke. Extensive experimental research has shown that the smaller the momentum when the valve collides with the partition, the smaller the force between the two. The momentum I during the collision between the valve and the partition is limited to: To ensure compressor reliability, momentum I < 0.01 kg.m / s; to further improve compressor reliability, momentum I ≤ 0.005 kg.m / s. To achieve the goal of limiting momentum I, a feasible method is to reduce the valve density ρ. The valve material can be made of materials with a lower density than steel, such as titanium alloys, aluminum alloys, and other lightweight materials. Suitable material density ρ is < 5000 kg / m^3, which reduces the mass of the valve body, improves valve reliability during collisions, and effectively controls valve wear.

[0134] like Figure 10 The valve body of the present invention is made of lightweight materials. After testing, the momentum formula is adopted, and the valve density ρ is used as the only variable. The relationship between the material density and wear of the valve is fitted with a curve. As the density of the valve material increases, its wear decreases. When the density is greater than 3000kg / m^3, it basically tends to a stable state without wear. Therefore, the optimal range of the valve body density is (3000kg / m^3, 5000kg / m^3).

[0135] In some embodiments,

[0136] The air-supplementing and reheat-increasing compressor is a two-cylinder compressor, wherein the cylinder 1 includes an upper cylinder 11 and a lower cylinder 12, and the partition plate or flange 2 is a partition plate (or flange, i.e., the air-supplementing channel and the reheat-increasing port can be opened on the partition plate or on the flange) provided between the upper cylinder 11 and the lower cylinder 12. The upper cylinder 11 is provided with a pressure introduction groove 71, a valve groove 61, and an injection channel 51. The valve body 3 includes a valve body 31 and a valve body 32. At least a portion of the structure of the valve body 31 is provided in the valve groove 61, and at least a portion of the structure of the valve body 31 is provided in the injection channel 51. The valve body 31 can move in the valve groove 61 and the injection channel 51 to open or close the injection channel 51.

[0137] The lower cylinder 12 is provided with a second pressure introduction groove 72, a second valve groove 62, and a second injection channel 52. At least a portion of the second valve body 32 is disposed in the second valve groove 62, and at least a portion of the second valve body 32 is disposed in the second injection channel 52. The second valve body 32 can move in the second valve groove 62 and the second injection channel 52 to open or close the second injection channel 52.

[0138] The enthalpy increase port 8 includes an enthalpy increase port 1 81 and an enthalpy increase port 2 82. The enthalpy increase port 1 81 is opened from the axial end face of the partition facing the upper cylinder 11 in the direction toward the interior of the partition, and is connected to the air-supplementing enthalpy increase channel 4. The enthalpy increase port 2 82 is opened from the axial end face of the partition facing the lower cylinder 12 in the direction toward the interior of the partition, and is connected to the air-supplementing enthalpy increase channel 4.

[0139] This is a further preferred structural form of the air-supply and reheat-increasing compressor of the present invention, that is, a double-cylinder structure of the upper and lower cylinders. Through the connection between the upper end of the air-supply and reheat-increasing channel and the injection channel one, valve body one, etc., and the connection between the lower end of the air-supply and reheat-increasing channel and the injection channel two, valve body two, etc., the effect of increasing the enthalpy of the upper and lower cylinders can be achieved respectively, and the function of automatic air supply can be achieved according to the size relationship between the respective compression chamber pressures and the air supply pressures. The air supply time can be adaptively adjusted according to the size of the working conditions, which solves the problem of poor enthalpy increase effect caused by unreasonable enthalpy increase time; and it can increase the air supply volume for both cylinders, reduce stress concentration, and reduce noise.

[0140] like Figure 12 , in some embodiments,

[0141] The air-compensating and reheat-increasing compressor is a single-cylinder compressor. The partition plate or flange 2 includes an upper flange 21 and a lower flange 22. The cylinder 1 is provided with the pressure introduction groove 7, the valve groove 6 and the injection channel 5. At least part of the structure of the valve body 3 is disposed in the valve groove 6, and at least part of the structure of the valve body 3 is disposed in the injection channel 5. The valve body 3 can move in the valve groove 6 and the injection channel 5 to open or close the injection channel 5.

[0142] The enthalpy increase port 8 and the air-supplementing enthalpy increase channel 4 are arranged on the upper flange 21 or the lower flange 22. The enthalpy increase port 8 is opened from the axial end surface of the upper flange 21 or the lower flange 22 facing the cylinder 1 in the internal direction of the upper flange 21 or the lower flange 22 to communicate with the air-supplementing enthalpy increase channel 4.

[0143] This is a further preferred structural form of the air-increasing and enthalpy-increasing compressor of the present invention, namely a single-cylinder structure. By connecting the air-increasing and enthalpy-increasing channel with the injection channel, valve body, etc., it can achieve the effect of enthalpy-increasing and air-increasing on a single cylinder, and can realize the function of automatic air-increasing according to the size relationship between the pressure of a single compression chamber and the air-increasing pressure. It can adaptively adjust the air-increasing time according to the size of the working conditions, and solve the problem of poor enthalpy-increasing effect caused by unreasonable enthalpy-increasing time; and it can increase the air-increasing amount, reduce stress concentration, and reduce noise for a single cylinder. Figure 7 for Figure 1A partial enlarged view of the assembly position relationship of the middle valve on the pump body shows that: when the cylinder valve slot has less constraint on the valve, the valve has a larger inclination angle α when colliding with the partition (upper end), and the corresponding contact area between the valve and the partition is smaller; when the cylinder valve slot has greater constraint on the valve, the valve has a smaller inclination angle α when colliding with the partition (lower end), and the corresponding contact area between the valve and the partition is larger.

[0144] The compressor structure to which the present invention relates: The present invention relates to a rolling rotor type compressor, which includes a liquid separator, an enthalpy increasing component, a casing, a motor, and a pump body assembly. The liquid separator is arranged outside the casing and is used to transport low-pressure refrigerant to the pump body assembly. The casing wraps the motor and the pump body assembly and forms an airtight isolation with the external environment. The motor is fixed to the upper part of the casing by interference fit, and the pump body assembly is arranged at the lower part of the motor. When the compressor is a single-cylinder compressor, the pump body assembly includes an upper flange, a cylinder, a lower flange, a crankshaft, a roller and a vane; when the compressor is a two-cylinder or multi-cylinder compressor, the pump body assembly includes an upper flange, a cylinder, a partition, a lower flange, a crankshaft, a roller and a vane, and a plurality of cylinders are arranged at intervals between the flange (upper flange or lower flange) and the partition. The roller is located on the inner circle of the cylinder and is sleeved on the eccentric circle of the crankshaft, rotating in the cylinder with the crankshaft. The vane is slidably arranged in the cylinder vane groove, and one end thereof abuts against the outer circle of the roller. As the roller rotates, the volume of the compression chamber gradually decreases. When the pressure in the compression chamber is greater than or equal to the exhaust pressure, the refrigerant is discharged from the pump body.

[0145] The enthalpy-increasing structure of the present invention comprises one or more valve slots disposed on the pump body. The first side of the valve slot is connected to the cylinder exhaust oblique cutout via the compression chamber pressure introduction channel, and the second side of the valve slot is provided with an injection channel connected to the compression chamber. The valve is confined to move between the cylinder valve slot and the adjacent partition (for single-cylinder compressors, the component adjacent to the valve slot is the lower flange). The enthalpy-increasing component is disposed outside the housing, and its lower bend passes through the housing and sequentially connects to the enthalpy-increasing channel, enthalpy-increasing port, and injection channel on the pump body. The valve size φd is designed to be larger than the enthalpy-increasing port and smaller than the valve slot size φD to ensure that the valve can move freely within the valve chamber while covering the enthalpy-increasing port, thereby achieving closure of the enthalpy-increasing port.

[0146] Enthalpy increase process: Medium-pressure refrigerant is introduced from the system into the enthalpy increase component. This medium pressure is higher than the suction pressure and lower than the exhaust pressure. When the compression chamber pressure is lower than the medium pressure, the pressure on the valve side close to the enthalpy increase port is higher than the pressure on the side away from the enthalpy increase port. The valve moves away from the enthalpy increase port, the enthalpy increase port opens, and the medium-pressure refrigerant passes through the enthalpy increase component, the enthalpy increase channel, the enthalpy increase port, and the injection channel in sequence to enter the compression chamber. When the compression chamber pressure is higher than the medium pressure, the pressure on the valve side close to the enthalpy increase port is lower than the pressure on the side away from the enthalpy increase port. The valve moves toward the enthalpy increase port, and the enthalpy increase port closes, preventing the refrigerant in the compression chamber from flowing out.

[0147] The present invention also provides an air conditioner, which includes the aforementioned air-supplementing and enthalpy-increasing compressor.

[0148] The above description is merely a preferred embodiment of the present invention and is not intended to limit the present invention. Any modifications, equivalent substitutions, and improvements made within the spirit and principles of the present invention shall be included within the scope of protection of the present invention. The above description is merely a preferred embodiment of the present invention. It should be noted that those skilled in the art can make various improvements and variations without departing from the technical principles of the present invention, and such improvements and variations shall also be considered within the scope of protection of the present invention.

Claims

1. An air-injection and enthalpy-increasing compressor, characterized in that: include: A cylinder (1), a partition or flange (2) and a valve body (3), wherein the partition or flange (2) is connected to an axial end face of the cylinder (1), and an air supply enthalpy increasing channel (4) is provided inside the partition or flange (2), and an injection channel (5) is provided in a recessed manner on an axial end face of the cylinder (1) connected to the partition or flange (2), or an injection channel (5) is provided in a recessed manner on an axial end face of the partition or flange (2) connected to the cylinder (1); A valve groove (6) is also provided on the cylinder (1) at a position connected to the injection channel (5), the radial inner side of the injection channel (5) is connected to the internal cavity of the cylinder (1), at least part of the structure of the valve body (3) is arranged in the valve groove (6), and a pressure introduction groove (7) is also provided on the side of the valve groove (6) away from the injection channel (5), one end of the pressure introduction groove (7) is connected to the valve groove (6), and the other end can be connected to the internal cavity of the cylinder (1), and the valve body (3) can move in the valve groove (6) and the injection channel (5) to open or close the injection channel (5); the surface hardness value of the valve body (3) is H, the surface hardness value of the partition or flange (2) is H1, and B=H1 / H∈(0.2, 2).

2. The air-compensating and enthalpy-increasing compressor according to claim 1, characterized in that: It also includes a roller (15), which is arranged in the cylinder. The partition or flange (2) is made of a modulated steel material, and its hardness value H1 satisfies: 23HRC≤H1≤60HRC. The material of the roller (15) is gray cast iron, and its hardness value is 18~20HRC.

3. The air-injection and enthalpy-increasing compressor according to claim 1, characterized in that: The pressure introduction groove (7) can introduce the refrigerant in the internal cavity of the cylinder (1) and act on one end of the valve body (3), and the air-supply enthalpy-increasing channel (4) can introduce the refrigerant and act on the other end of the valve body (3). When the refrigerant pressure introduced by the pressure introduction groove (7) is less than the refrigerant pressure in the air-supply enthalpy-increasing channel (4), the valve body (3) moves toward the direction of the pressure introduction groove (7) and then opens the injection channel (5). When the refrigerant pressure introduced by the pressure introduction groove (7) is greater than the refrigerant pressure in the air-supply enthalpy-increasing channel (4), the valve body (3) moves toward the direction of the injection channel (5) and then closes the injection channel (5). When the injection channel (5) is opened, the refrigerant in the air-supply enthalpy-increasing channel (4) can be replenished into the internal cavity of the cylinder (1) through the injection channel (5).

4. The air-compensating and enthalpy-increasing compressor according to claim 1, characterized in that: An exhaust bevel cutout (9) is provided on the axial end face of the cylinder (1) away from the partition or flange (2), and the radial inner side of the exhaust bevel cutout (9) is connected to the internal cavity of the cylinder (1). One end of the pressure introduction groove (7) extends to connect with the exhaust bevel cutout (9) to communicate with the internal cavity, so that the refrigerant in the internal cavity can be introduced into the pressure introduction groove (7).

5. The air-compensating and enthalpy-increasing compressor according to claim 1, characterized in that: The pressure introduction groove (7) extends along the axial direction of the cylinder (1), and the air-supplementing enthalpy-increasing channel (4) extends along the radial direction of the cylinder (1). An enthalpy-increasing port (8) is also provided on the partition or flange (2). The enthalpy-increasing port (8) extends from an axial end face of the partition or flange (2) toward the interior of the partition or flange (2) and extends to communicate with the air-supplementing enthalpy-increasing channel (4). The enthalpy-increasing port (8) is connected to the injection channel (5).

6. The air-compensating and enthalpy-increasing compressor according to claim 1, characterized in that: In the projection surface of the longitudinal plane, in the axial direction perpendicular to the cylinder (1), the width of the pressure introduction groove (7) is smaller than the width of the valve groove (6), the width of the valve groove (6) is smaller than the width of the injection channel (5), and the width of the valve body (3) in the axial direction perpendicular to the cylinder (1) is smaller than the width of the valve groove (6) in the same direction, so that a clearance fit is formed between the valve body (3) and the valve groove (6).

7. The air-compensating and enthalpy-increasing compressor according to any one of claims 1 to 6, characterized in that: An end face of the valve body (3) facing the partition or flange (2) is a first end face, and an axial end face of the partition or flange (2) facing the cylinder (1) is a second end face, wherein the maximum distance between the first end face and the second end face is a stroke L of the valve body (3), and L is set to: 0.05mm≤L≤1.5mm.

8. The air-compensating and enthalpy-increasing compressor according to any one of claims 1 to 6, characterized in that: The valve body (3) is a cylindrical structure, the valve slot (6), the pressure introduction slot (7) and the injection channel (5) are also cylindrical structures, one end face of the valve body (3) facing the partition or flange (2) is a plane, and one end face of the valve body (3) facing the pressure introduction slot (7) is also a plane. In the projection plane of the longitudinal plane, the valve body (3) is a rectangular structure, and the valve slot (6), the pressure introduction slot (7) and the injection channel (5) are also rectangular structures.

9. The air-compensating and enthalpy-increasing compressor according to claim 8, characterized in that: 0.01mm≤λ≤0.1mm; Wherein λ is the gap between the valve slot (6) and the valve body (3) in a direction perpendicular to the central axis of the valve slot (6), that is, the valve slot diameter minus the valve body diameter.

10. The air-compensating and enthalpy-increasing compressor according to claim 8, characterized in that: d is the diameter of the valve body (3), 4mm≤d<12mm.

11. The air-compensating and enthalpy-increasing compressor according to claim 8, characterized in that: h is the length of the valve body (3) on its central axis, that is, the thickness of the valve body, 1mm≤h<3mm.

12. The air-compensating and enthalpy-increasing compressor according to claim 8, characterized in that: ρ is the valve body density, ρ<5000kg / m^3.

13. The air-compensating and enthalpy-increasing compressor according to claim 8, characterized in that: L is the valve body stroke, L≤0.6mm.

14. The air-compensating and enthalpy-increasing compressor according to claim 8, characterized in that: An end face of the valve body (3) facing the partition or flange (2) is a first end face, and an end face of the cylinder (1) facing the partition or flange (2) is a third end face, wherein the minimum distance between the first end face and the third end face is h0, h is the length of the valve body (3) on its central axis, and h0 / h<0.

5.

15. The air-compensating and enthalpy-increasing compressor according to claim 5, characterized in that: The air-supplementing and enthalpy-increasing compressor is a two-cylinder compressor, wherein the cylinder (1) includes an upper cylinder (11) and a lower cylinder (12), the partition or flange (2) is a partition arranged between the upper cylinder (11) and the lower cylinder (12), the upper cylinder (11) is provided with a pressure introduction groove (71), a valve groove (61) and an injection channel (51), the valve body (3) includes a valve body (31) and a valve body (32), at least part of the structure of the valve body (31) is arranged in the valve groove (61), at least part of the structure of the valve body (31) is arranged in the injection channel (51), and the valve body (31) can move in the valve groove (61) and the injection channel (51) to open or close the injection channel (51); The lower cylinder (12) is provided with a second pressure introduction groove (72), a second valve groove (62) and a second injection channel (52); at least a portion of the structure of the second valve body (32) is disposed in the second valve groove (62); at least a portion of the structure of the second valve body (32) is disposed in the second injection channel (52); the second valve body (32) can move in the second valve groove (62) and the second injection channel (52) to open or close the second injection channel (52); The enthalpy increase port (8) includes an enthalpy increase port 1 (81) and an enthalpy increase port 2 (82). The enthalpy increase port 1 (81) is opened from the axial end surface of the partition plate facing the upper cylinder (11) in the direction toward the interior of the partition plate to communicate with the air-supplementing enthalpy increase channel (4). The enthalpy increase port 2 (82) is opened from the axial end surface of the partition plate facing the lower cylinder (12) in the direction toward the interior of the partition plate to communicate with the air-supplementing enthalpy increase channel (4).

16. The air-compensating and enthalpy-increasing compressor according to claim 5, characterized in that: The air-supplementing and enthalpy-increasing compressor is a single-cylinder compressor, the partition or flange (2) includes an upper flange (21) and a lower flange (22), the cylinder (1) is provided with the pressure introduction groove (7), the valve groove (6) and the injection channel (5), at least part of the structure of the valve body (3) is arranged in the valve groove (6), at least part of the structure of the valve body (3) is arranged in the injection channel (5), and the valve body (3) can move in the valve groove (6) and the injection channel (5) to open or close the injection channel (5); The enthalpy increasing port (8) and the air-supplementing enthalpy increasing channel (4) are arranged on the upper flange (21) or the lower flange (22), and the enthalpy increasing port (8) is opened from the axial end surface of the upper flange (21) or the lower flange (22) facing the cylinder (1) in the direction toward the interior of the upper flange (21) or the lower flange (22) to communicate with the air-supplementing enthalpy increasing channel (4).

17. An air conditioner, characterized in that: The invention comprises the air-supplementing and enthalpy-increasing compressor according to any one of claims 1 to 16.

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