Scroll rotor type compressor cylinder and compressor

Abstract

The present invention provides a rolling piston compressor cylinder and a compressor. The cylinder includes a cylinder block, and a piston rotates within the cylinder block. The cylinder block is provided with a vane slot, and a vane is used to divide the internal space of the cylinder block into a suction chamber and a compression chamber. The cylinder further includes: a suction hole provided on the cylinder block and communicating with the suction chamber. The suction hole has a first flow path and a second flow path. The refrigerant entering the suction chamber along the first flow path at least has a state of avoiding the piston and being ejected to the distal end of the suction chamber away from the suction hole. This application can reduce the suction resistance loss of the cylinder, thereby reducing the energy consumption of the compressor. At the same time, it can improve the impact of the gas just inhaled into the cylinder on the piston, thereby improving the efficiency of the compressor.

Description

Technical Field

[0001] The present invention relates to the technical field of rolling rotor compressors, and more particularly to a cylinder of a rolling rotor compressor and a compressor. Background Art

[0002] A rolling rotor compressor is a positive displacement compressor, mainly composed of a housing, a motor, a crankshaft, a piston, a cylinder, and a vane, etc. The piston is located inside the cylinder. When the crankshaft rotates around the rotation center, the piston rotates closely along the inner surface of the cylinder. Thus, a crescent-shaped space can be formed between the outer surface of the piston and the inner surface of the cylinder. The vane moving up and down divides this space range into two independent parts, one part is the suction chamber, and the other part is the compression chamber. The vane is pressed against the outer surface of the piston by a spring.

[0003] In the existing rolling rotor compressor, the center line of the suction hole of the cylinder is directly opposite to the center of the cylinder (as Figure 1 ). In this structure, when sucking air, the gas shoots into the cylinder radially from the suction hole, directly hits the piston, and then moves circumferentially counterclockwise along the outer wall of the piston and the inner wall of the cylinder. The gas flow direction changes from the cylinder radial direction to the cylinder circumferential direction, and the flow resistance loss is very large, that is, the suction resistance loss is large, which will cause the refrigerating capacity of the compressor to decrease and the efficiency to decrease. Summary of the Invention

[0004] In view of this, the present invention provides a cylinder of a rolling rotor compressor and a compressor, which can reduce the suction resistance loss of the cylinder, thereby reducing the energy consumption of the compressor; at the same time, it can improve the impact effect of the gas just inhaled into the cylinder on the piston, thereby improving the efficiency of the compressor.

[0005] According to one aspect of the present invention, there is provided a cylinder of a rolling rotor compressor. The cylinder includes a cylinder block, a piston rotates inside the cylinder block, the cylinder block is provided with a vane groove, and the piston cooperates with the vane to divide the internal space of the cylinder block into a suction chamber and a compression chamber; the cylinder further includes:

[0006] A suction hole is provided on the cylinder block and communicates with the suction chamber. The suction hole has a first flow channel and a second flow channel. The refrigerant entering the suction chamber along the first flow channel has at least a state of avoiding the piston and being sprayed to the far end of the suction chamber away from the suction hole.

[0007] Preferably, the projection of the side wall of the suction hole with the largest distance from the vane groove on the plane where the upper surface of the cylinder block is located is a first line segment, and the projection of the outer surface of the piston on the plane where the upper surface of the cylinder block is located is a first contour line. In a partial state of the piston, a gap channel is formed between the extension line of the first line segment and a tangent line of the first contour line.

[0008] Preferably, when the piston is at the farthest end from the vane slot, the angle between the first line segment and the center line of the vane slot is greater than 90 degrees and not greater than 180 degrees.

[0009] Preferably, the center line of the suction hole is parallel to the center line of the vane slot.

[0010] Preferably, the suction hole is cylindrical.

[0011] Preferably, a spring hole is further provided at the end of the vane slot on the cylinder block. The vane slot communicates with the spring hole, and a spring for pressing the vane against the outer surface of the piston is provided in the spring hole.

[0012] Preferably, the minimum distance between the suction hole and the spring hole is greater than or equal to 1 mm.

[0013] Preferably, the center line of the spring hole and the spring are located on the central plane of the vane slot.

[0014] Preferably, the center line of the spring hole passes through the center of the cylinder block.

[0015] According to another aspect of the present invention, a compressor is provided, and the compressor includes the rolling rotor type compressor cylinder according to any one of the above.

[0016] The beneficial effects of the present invention compared with the prior art are as follows:

[0017] For the rolling rotor type compressor cylinder and the compressor provided by the present invention, the refrigerant flowing through the first flow channel can avoid the piston and be directly sprayed to the far end of the suction cavity, instead of being radially injected into the cylinder and directly hitting the piston. The degree of change in the flow direction of the gaseous refrigerant is smaller than that of the prior art, thereby reducing the suction resistance of the cylinder, reducing the energy consumption of the compressor, and improving the refrigerating capacity and efficiency of the compressor; on the other hand, the impact force of the gas entering the cylinder on the piston is reduced, so that the hindering effect of the impact force on the rotation of the piston is reduced, and further the compressor efficiency is improved. Description of the Drawings

[0018] The drawings here are incorporated into the specification and constitute a part of this specification, showing the embodiments in line with the present invention, and are used together with the specification to explain the principles of the present invention. Obviously, the drawings in the following description are only some embodiments of the present invention, and those of ordinary skill in the art can also obtain other drawings based on these drawings without creative efforts.

[0019] Figure 1 It is a schematic structural diagram of a rolling rotor type compressor cylinder in the prior art;

[0020] Figure 2Schematic structural diagram of a cylinder of a rolling rotor compressor disclosed in this embodiment;

[0021] Figure 3 Schematic diagram of the position of the suction hole of the cylinder of the rolling rotor compressor disclosed in this embodiment;

[0022] Figure 4 is Figure 3 Schematic diagram of the included angle formed between the extension line L2 of the first line segment and the center line S of the vane slot in Detailed implementation manners

[0023] Example embodiments will now be described more fully with reference to the accompanying drawings. However, the example embodiments can be implemented in various forms and should not be construed as limited to the embodiments set forth herein. On the contrary, these embodiments are provided so that this invention will be thorough and complete, and will fully convey the concept of the example embodiments to those skilled in the art. The features, structures, or characteristics described may be combined in any suitable manner in one or more embodiments. In the following description, numerous specific details are provided to give a thorough understanding of the embodiments of the present disclosure. However, those skilled in the art will realize that the technical solutions of the present disclosure can be practiced without one or more of the specific details, or other methods, materials, devices, etc. may be employed. In other cases, well-known technical solutions are not shown or described in detail to avoid obscuring aspects of the present disclosure. The same reference numerals in the drawings denote the same or similar structures, and thus their detailed descriptions will be omitted.

[0024] The terms "a", "an", "the", "said" and "at least one" are used to denote the presence of one or more elements / components / etc.; the terms "comprising", "having" and "provided with" are used to denote an open inclusion meaning and mean that there may be additional elements / components / etc. in addition to the listed elements / components / etc.

[0025] Figure 1 Schematic structural diagram of a cylinder of a rolling rotor compressor in the prior art. As Figure 1 shown, in the prior art, when the rolling rotor compressor is working, gas enters the cylinder from the suction hole 104, the motor drives the crankshaft, and the crankshaft drives the piston to perform a rotary motion, thereby compressing the gas. The compressed high-pressure gas is discharged from the cylinder through the exhaust port and enters the compressor housing. When the rolling rotor compressor is inhaling, the gaseous refrigerant shoots into the cylinder radially from the suction hole 104, directly hits the piston 101, and then moves circumferentially counterclockwise along the outer wall of the piston 101 and the inner wall of the cylinder. Therefore, the compressor needs to do additional work to change the gas flow direction from the cylinder radial direction to the cylinder circumferential direction, and the flow resistance loss is very large, resulting in an increase in the suction energy consumption of the compressor and a decrease in the suction efficiency.

[0026] Figure 2 Schematic diagram of the cylinder structure of a rolling rotor compressor disclosed in this application. As Figure 2 shown, the present invention discloses a cylinder of a rolling rotor compressor. The cylinder includes a cylinder block 103. A piston 101 in the compressor equipped with this cylinder rotates within the above-mentioned cylinder block 103. The above-mentioned piston 101 cooperates with a vane 102 to divide the internal space of the cylinder block 103 into a suction chamber 107 and a compression chamber 108. A vane slot 106 is provided on the above-mentioned cylinder block 103.

[0027] The above-mentioned cylinder disclosed in this embodiment further includes a suction hole 104. The above-mentioned suction hole 104 is provided on the above-mentioned cylinder block 103 and communicates with the above-mentioned suction chamber 107. The suction hole 104 is a through hole penetrating the cylinder block 103 of the cylinder. The above-mentioned suction hole 104 has a first flow channel A and a second flow channel B. The refrigerant entering the above-mentioned suction chamber 107 along the above-mentioned first flow channel A at least has a state of avoiding the above-mentioned piston 101 and being sprayed to the far end of the above-mentioned suction chamber 107 away from the above-mentioned suction hole 104. In this way, the gaseous refrigerant in the first flow channel A can flow more smoothly into the interior of the cylinder block 103, and then perform a circumferential flow in the counterclockwise direction. The degree of change in the flow direction of the gaseous refrigerant is smaller, and the impact of the gaseous refrigerant on the piston 101 is avoided.

[0028] The gaseous refrigerant entering from the second flow channel B is sprayed onto the outer surface of the piston 101 along a non-radial path. In this way, the refrigerant in the first flow channel A can completely avoid the piston 101 under certain conditions, and the injection direction of the refrigerant in the second flow channel B is non-radial, both of which make the degree of change in the flow direction of the refrigerant in the suction hole 104 smaller than that of the prior art, and the suction energy consumption can be reduced.

[0029] In this embodiment, at the end of the vane slot 106 on the above-mentioned cylinder block 103, that is, at the end away from the piston 101, a spring hole 105 is provided. The vane slot 106 communicates with the spring hole 105. The projection of the tube wall on the side of the above-mentioned suction hole 104 with the largest distance from the above-mentioned vane slot 106 on the plane where the upper surface of the above-mentioned cylinder block 103 is located is a first line segment. The projection of the outer surface of the above-mentioned piston 101 on the plane where the upper surface of the above-mentioned cylinder block 103 is located is a first contour line. In some states of the piston 101, for example, when the distance between the piston 101 and the vane slot 106 of the compressor is the largest, a gap channel 110 is formed between the extension line of the above-mentioned first line segment and a tangent line of the above-mentioned first contour line. The gap channel 110 is also the extended channel of the above-mentioned first flow channel A.

[0030] In this embodiment, the projection of the interface between the above-mentioned first flow channel A and the above-mentioned second flow channel B on the plane where the upper surface of the above-mentioned cylinder block 103 is located is a second line segment. The projection of the tube wall on the side of the above-mentioned suction hole 104 with the smallest distance from the above-mentioned spring hole 105 on the plane where the upper surface of the above-mentioned cylinder block 103 is located is a third line segment.

[0031] In a partial state of the piston 101, in the above-mentioned clearance channel 110, that is, in the region between the extension line of the first line segment and the extension line of the second line segment in the suction chamber 107, the distance between the inner walls on both sides of the cylinder block 103 in the first direction gradually increases in the second direction. And in the region between the extension line of the second line segment and the extension line of the third line segment, the distance between the inner wall of the cylinder block 103 and the outer surface of the piston 101 in the first direction gradually increases in the second direction. The first direction is the extending direction of the length direction of the blade groove 106. The second direction is perpendicular to the first direction and points from the suction hole 104 to the spring hole 105.

[0032] Please continue to refer to Figure 3 , when the piston 101 is at the farthest end from the blade groove 106, the angle between the extension line of the first line segment and the center line of the blade groove 106 is greater than 90 degrees and not greater than 180 degrees. Optionally, as shown in Figure 3 , in one embodiment, the first line segment is Figure 3 L1 in Figure 3 , and the center line of the blade groove 106 is Figure 3 S in Figure 4 , and the angle between L1 and S is 180 degrees. In another embodiment, the first line segment is Figure 3 and Figure 4 L2 in Figure 4 , and the angle between L2 and S is greater than 90 degrees and less than 180 degrees. Specifically, please refer to Figure 4 , and the angle r formed by the intersection of the end of L2 far from the piston and the end of S far from the piston is greater than 90 degrees and less than 180 degrees. When the position of the first line segment changes from L2 to L1, the angle between the extension line of the first line segment and the center line of the blade groove 106 is also continuously increasing. Until the first line segment is in the state of Figure 3 , the angle between the extension line of the first line segment and the center line of the blade groove 106 reaches 180 degrees. Optionally, the center line of the suction hole 104 is parallel to the center line of the blade groove 106.

[0033] In this embodiment, the suction hole 104 is cylindrical, and the center line of the suction hole 104 is parallel to the center line of the spring hole 105. The blade groove 106 communicates with the spring hole 105. A spring 109 for pressing the blade 102 against the outer surface of the piston 101 is provided in the spring hole 105. The center line of the spring hole 105 and the spring are located on the central plane of the blade groove 106. The center line of the spring hole 105 passes through the center of the cylinder block 103.

[0034] As a preferred embodiment of the present application, the minimum distance between the above-mentioned air suction hole 104 and the above-mentioned spring hole 105 is greater than or equal to 1 mm. In this way, while minimizing the angle between the air suction hole 104 and the spring hole 105 and reducing the air suction loss, the strength of the cylinder block 103 is ensured to meet the production requirements. It should be noted that the present application does not limit the distance between the above-mentioned air suction hole 104 and the spring hole 105.

[0035] The embodiment of the present invention also provides a compressor, which includes the rolling rotor type compressor cylinder disclosed in any of the above embodiments. Among them, the detailed structural features and advantages of the rolling rotor type compressor cylinder can be referred to the description of the above embodiments, and will not be elaborated here.

[0036] In summary, the rolling rotor type compressor cylinder and the compressor disclosed in this embodiment have at least the following advantages:

[0037] The rolling rotor type compressor cylinder and the compressor disclosed in this embodiment enable the refrigerant flowing through the first flow channel to avoid the piston and directly spray to the far end of the suction cavity, instead of radially injecting into the cylinder and directly hitting the piston. This makes the degree of change in the flow direction of the gaseous refrigerant smaller than that of the prior art, thereby reducing the air suction resistance of the cylinder, reducing the energy consumption of the compressor, and improving the refrigerating capacity and efficiency of the compressor; on the other hand, it reduces the impact force of the gas entering the cylinder on the piston, reduces the hindrance of this impact force to the rotation of the piston, and further improves the efficiency of the compressor.

[0038] In the description of the present invention, it should be understood that the orientation or positional relationship indicated by the terms "bottom", "longitudinal", "transverse", "upper", "lower", "front", "rear", "vertical", "horizontal", etc. is based on the orientation or positional relationship shown in the drawings, and is only for the convenience of describing the present invention and simplifying the description, rather than indicating or implying that the structure or element referred to must have a specific orientation, be constructed and operated in a specific orientation, and therefore cannot be understood as a limitation of the present invention. In addition, the features defined with "first", "second" may explicitly or implicitly include one or more of such features. In the description of the present invention, unless otherwise specified, the meaning of "a plurality" is two or more, and the meaning of "several" is one or more.

[0039] In the description of this specification, the descriptions referring to terms such as "one embodiment", "some embodiments", "schematic embodiments", "examples", "specific examples", etc. mean that the specific features, structures, materials or characteristics described in connection with the embodiment or example are included in at least one embodiment or example of the present invention. In this specification, the schematic expressions of the above terms do not necessarily refer to the same embodiment or example. Moreover, the specific features, structures, materials or characteristics described can be combined in a suitable manner in any one or more embodiments or examples.

[0040] The above content is a further detailed description of the present invention in combination with specific preferred embodiments. It cannot be determined that the specific implementation of the present invention is only limited to these descriptions. For those of ordinary skill in the technical field to which the present invention pertains, without departing from the concept of the present invention, several simple deductions or substitutions can still be made, and all should be regarded as belonging to the protection scope of the present invention.

Claims

1. A rolling rotor type compressor cylinder, the cylinder comprising a cylinder block (103), a piston (101) rotating within the cylinder block (103), the cylinder block (103) being provided with a vane slot (106), and the piston (101) cooperating with a vane (102) to divide the internal space of the cylinder block (103) into a suction chamber (107) and a compression chamber (108); characterized in that, The cylinder further includes: An intake hole (104) is provided on the cylinder block (103) and communicates with the intake chamber (107). The intake hole (104) has a first flow channel and a second flow channel. The refrigerant entering the intake chamber (107) along the first flow channel is at least in a state of avoiding the piston (101) and being sprayed to the distal end of the intake chamber (107) away from the intake hole (104). The gaseous refrigerant entering the intake chamber (107) from the second flow channel is sprayed onto the outer surface of the piston (101) along a non-radial path. The center line of the intake hole (104) is parallel to the center line of the vane slot (106). A spring hole (105) is further formed at the end of the vane slot (106) on the cylinder block (103). The minimum distance between the intake hole (104) and the spring hole (105) is greater than or equal to 1 mm. The projection of the tube wall of the intake hole (104) on the side with the largest distance from the vane slot (106) on the plane of the upper surface of the cylinder block (103) is a first line segment. The projection of the outer surface of the piston (101) on the plane of the upper surface of the cylinder block (103) is a first contour line. When the distance between the piston (101) and the vane slot (106) of the compressor is the largest, a gap channel (110) is formed between the extension line of the first line segment and a tangent line of the first contour line.

2. The rolling rotor type compressor cylinder according to claim 1, wherein, When the piston (101) is at the farthest end from the vane slot (106), the angle between the first line segment and the center line of the vane slot (106) is greater than 90 degrees and not greater than 180 degrees.

3. The rolling rotor type compressor cylinder according to claim 1, wherein The intake hole (104) is cylindrical.

4. The rolling rotor type compressor cylinder according to claim 1, wherein, The vane slot (106) communicates with the spring hole (105). A spring for pressing the vane (102) against the outer surface of the piston (101) is provided in the spring hole (105).

5. The rolling rotor type compressor cylinder according to claim 4, wherein, The center line of the spring hole (105) and the spring are located on the central plane of the vane slot (106).

6. The rolling rotor type compressor cylinder according to claim 5, wherein, The center line of the spring hole (105) passes through the center of the cylinder block (103).

7. A compressor, characterized in that, The compressor includes a rolling piston type compressor cylinder as described in any one of claims 1-6.

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