A variable-frequency compressor

Abstract

The present invention provides a variable frequency compressor. The intermediate plate is provided with a lower exhaust refrigerant passage hole, a groove, a first hole, a rotary valve, a guide vane, a spring hole, an elastic element and a push head; the lower exhaust refrigerant passage hole communicates with the refrigerant passage hole on the first cylinder; the groove is arranged on the first end surface of the intermediate plate, and the groove penetrates the first end surface but does not penetrate the second end surface; the first hole communicates with the second position of the inner cavity of the first cylinder; the rotary valve is rotatable in the first hole; the rotation of the rotary valve is used to control the notch to be in the communication position or the closed position; the guide vane is inclined and installed on the rotary valve; the thrust of the push head on the rotary valve drives the notch to communicate with the second position. When the rotational speed of the variable frequency compressor is less than the critical speed, the variable frequency compressor is in the small capacity mode, the motor speed is relatively high, the efficiency is high, the oil return efficiency of the pump body is high and the overall vibration is reduced; when the rotational speed of the variable frequency compressor is greater than the critical speed, the variable frequency compressor is in the full capacity mode.

Description

Technical Field

[0001] The present invention relates to the technical field of compressors, and particularly to a variable-frequency compressor. Background Art

[0002] A variable-frequency compressor includes a motor and a pump body. The pump body includes a crankshaft, a piston, and a cylinder; the crankshaft includes an eccentric portion and a long shaft, and the piston is mounted on the eccentric portion of the crankshaft; the long shaft of the crankshaft is connected to the rotating shaft of the motor, and the motor drives the crankshaft to rotate. The rotation of the crankshaft causes the piston to rotate along the inner wall of the cylinder within the cylinder. Since the volume inside the cylinder is constant, whether the piston rotates quickly for one circle or slowly for one circle, the suction volume and the discharge volume of the cylinder are equal.

[0003] When a variable-frequency compressor operates under the same working conditions, the refrigerating capacity is basically proportional to the rotational speed. When the rotational speed is low, the efficiency of the motor is low, the oil return efficiency of the pump body is low, and the overall vibration is obvious, resulting in a reduction in the performance and reliability of the variable-frequency compressor. Summary of the Invention

[0004] The present invention provides a variable-frequency compressor to solve the technical problem of the reduction in performance and reliability of a variable-frequency compressor at low rotational speeds.

[0005] To solve the above technical problem, the present invention provides a variable-frequency compressor, including an intermediate plate and a first cylinder; the intermediate plate includes a first end face and a second end face, the first end face is used for connecting the first cylinder, and the second end face is not in communication with the inner cavity of the first cylinder; a refrigerant passage hole for refrigerant flow is provided on the cylinder wall of the first cylinder;

[0006] The intermediate plate is provided with a lower exhaust refrigerant passage hole, a groove, a first hole, a rotary valve, a guide vane, a spring hole, an elastic element, and a push head;

[0007] The lower exhaust refrigerant passage hole is in communication with the refrigerant passage hole on the first cylinder;

[0008] The groove is provided on the first end face of the intermediate plate, the groove penetrates the first end face but does not penetrate the second end face; one end of the groove is in communication with a first position of the inner cavity of the first cylinder, and the other end is in communication with the first hole; the first hole is in communication with a second position of the inner cavity of the first cylinder; the orthographic projections of the first position and the second position on the first end face do not coincide;

[0009] The rotary valve is installed in the first hole and is rotatable within the first hole. A sealed connection is provided between the rotary valve and the first hole. The rotary valve is provided with a notch, and the rotation of the rotary valve is used to control the notch to be in a communicating position or a closed position. When the notch is in the communicating position, the other end of the groove, the notch, and the second position are sequentially communicated. When the notch is in the closed position, the notch and the second position are not communicated.

[0010] The deflector is inclined and installed on the rotary valve. The horizontal distance between the top of the deflector and the push head is less than the horizontal distance between the bottom of the deflector and the push head. The deflector extends from the side of the rotary valve into the lower exhaust refrigerant passage hole.

[0011] The elastic element and the push head are installed in the spring hole. The push head abuts against the side surface of the rotary valve. The push head is installed between the rotary valve and the elastic element, and the elastic element is in a compressed state. The thrust of the push head on the rotary valve drives the notch to communicate with the second position.

[0012] Optionally, the first cylinder includes a vane groove and an air inlet. The vane groove and the air inlet are on the orthographic projection of the first end face of the intermediate plate. The connecting line between the center of the vane groove and the center of the lower exhaust refrigerant passage hole is the first connecting line, and the connecting line between the center of the intermediate plate and the center of the lower exhaust refrigerant passage hole is the second connecting line. The range of the included angle between the first connecting line and the second connecting line is between 0° and 20°. One end of the groove intersects with one end of the air inlet close to the inner cavity of the first cylinder.

[0013] Optionally, the shape of the intermediate plate is annular, and the first end face and the second end face of the intermediate plate are parallel. The groove includes a first part and a second part. The first part is one end of the groove, and the second part is the remaining part of the groove after removing the first part. The shape of the second part is arc-shaped, and the second part is located between the inner diameter and the outer diameter of the middle.

[0014] Optionally, the lower exhaust refrigerant passage hole intersects with the first hole.

[0015] Optionally, the first hole penetrates through the first end face and the second end face of the intermediate plate, and the axis of the first hole is parallel to the axis of the exhaust refrigerant passage hole.

[0016] Optionally, the notch on the rotary valve is located at the top of the rotary valve.

[0017] Optionally, the push head includes a front end and a rear end. The shape of the front end is hemispherical, and the front end is in point contact with the side surface of the rotary valve; the shape of the rear end is cylindrical, and the rear end is connected to the elastic element.

[0018] Optionally, the side surface of the rotary valve includes a first plane for contacting the front end of the push head.

[0019] The present invention also provides another variable frequency compressor, which includes an upper cylinder head and a second cylinder; the upper cylinder head includes a first end face and a second end face. The first end face is used to connect the second cylinder, and the second end face is not communicated with the inner cavity of the second cylinder; a refrigerant passage hole for refrigerant flow is provided on the cylinder wall of the second cylinder;

[0020] The upper cylinder head is provided with a lower exhaust refrigerant passage hole, a groove, a first hole, a rotary valve, a guide vane, a spring hole, an elastic element and a push head;

[0021] The lower exhaust refrigerant passage hole is communicated with the refrigerant passage hole on the second cylinder;

[0022] The groove is provided on the first end face of the upper cylinder head. The groove penetrates the first end face but does not penetrate the second end face; one end of the groove is communicated with a first position of the inner cavity of the second cylinder, and the other end is communicated with the first hole; the first hole is communicated with a second position of the inner cavity of the second cylinder; the orthographic projections of the first position and the second position on the first end face do not coincide;

[0023] The rotary valve is installed in the first hole. The rotary valve is rotatable in the first hole, and the rotary valve is sealingly connected to the first hole; the rotary valve is provided with a notch. The rotation of the rotary valve is used to control the notch to be in a communicating position or a closed position. When the notch is in the communicating position, the other end of the groove, the notch and the second position are sequentially communicated. When the notch is in the closed position, the notch and the second position are not communicated;

[0024] The guide vane is inclinedly installed on the rotary valve. The horizontal distance between the top of the guide vane and the push head is less than the horizontal distance between the bottom of the guide vane and the push head; the guide vane extends from the side surface of the rotary valve into the lower exhaust refrigerant passage hole;

[0025] The elastic element and the push head are installed in the spring hole. The push head abuts against the side surface of the rotary valve. The push head is installed between the rotary valve and the elastic element, and the elastic element is in a compressed state; the thrust of the push head on the rotary valve drives the notch to be communicated with the second position.

[0026] The present invention also provides another variable frequency compressor, which includes a lower cylinder head and a third cylinder; the lower cylinder head includes a first end face and a second end face, the first end face is used to connect the third cylinder, and the second end face is not communicated with the inner cavity of the third cylinder; a refrigerant passage hole for refrigerant flow is provided on the cylinder wall of the third cylinder;

[0027] The lower cylinder head is provided with a lower exhaust refrigerant passage hole, a groove, a first hole, a rotary valve, a guide vane, a spring hole, an elastic element and a push head;

[0028] The lower exhaust refrigerant passage hole is communicated with the refrigerant passage hole on the third cylinder;

[0029] The groove is arranged on the first end face of the lower cylinder head, the groove penetrates the first end face but does not penetrate the second end face; one end of the groove is communicated with a first position of the inner cavity of the third cylinder, and the other end is communicated with the first hole; the first hole is communicated with a second position of the inner cavity of the third cylinder; the orthographic projections of the first position and the second position on the first end face do not coincide;

[0030] The rotary valve is installed in the first hole, the rotary valve can rotate in the first hole, and the rotary valve is sealingly connected with the first hole; the rotary valve is provided with a notch, and the rotation of the rotary valve is used to control the notch to be in a communication position or a closed position. When the notch is in the communication position, the other end of the groove, the notch and the second position are sequentially communicated. When the notch is in the closed position, the notch and the second position are not communicated;

[0031] The guide vane is obliquely installed on the rotary valve, and the horizontal distance between the top of the guide vane and the push head is less than the horizontal distance between the bottom of the guide vane and the push head; the guide vane extends from the side of the rotary valve into the lower exhaust refrigerant passage hole;

[0032] The elastic element and the push head are installed in the spring hole, the push head abuts against the side of the rotary valve, the push head is installed between the rotary valve and the elastic element, and the elastic element is in a compressed state; the thrust of the push head on the rotary valve drives the notch to be communicated with the second position.

[0033] The capacity of the variable-frequency compressor provided by the present invention can be changed. When the rotational speed of the variable-frequency compressor is less than the critical speed, since the torque of the refrigerant thrust on the rotary valve is less than the torque of the elastic element on the rotary valve, the notch is in the communication position. During the rotation of the piston in the first cylinder, the gas between the first position and the second position in the inner cavity of the first cylinder is not compressed. The volume of the gas compressed by the piston in one rotation decreases, the capacity of the variable-frequency compressor decreases, the variable-frequency compressor is in the small-capacity mode, the motor speed is relatively high, the efficiency is high, the oil return efficiency of the pump body is high, and the overall vibration is reduced, thereby improving the performance and reliability of the variable-frequency compressor; when the rotational speed of the variable-frequency compressor is greater than the critical speed, since the torque of the refrigerant thrust on the rotary valve is greater than the torque of the elastic element on the rotary valve, the notch is in the closed position, and the volume of the gas compressed by the piston in one rotation is equal to the volume of the gas compressed in the prior art, and the variable-frequency compressor is in the full-capacity mode. BRIEF DESCRIPTION OF THE DRAWINGS

[0034] Figure 1 FIG. is a schematic structural diagram of an intermediate plate provided by an embodiment of the present invention.

[0035] Figure 2 FIG. is a schematic structural diagram of a rotary valve and a guide vane after connection provided by an embodiment of the present invention.

[0036] Figure 3 is a top view of FIG.

[0037] Figure 4 FIG. is a schematic structural diagram of an intermediate plate and an upper cylinder after connection provided by an embodiment of the present invention.

[0038] Figure 5 is Figure 4 the top view of

[0039] Figure 6 FIG. is a schematic diagram of the position of the guide vane when the variable-frequency compressor provided by an embodiment of the present invention is in the half-capacity mode.

[0040] Figure 7 is Figure 6 a partial enlarged view of position A in

[0041] Figure 8 FIG. is a schematic diagram of the position of the guide vane when the variable-frequency compressor provided by an embodiment of the present invention is in the full-capacity mode.

[0042] Figure 9 is Figure 8 a partial enlarged view of position B in

[0043] Figure 10 is a front view Figure 1When, the schematic diagram of the decomposition of the force on the flow guide vane and the schematic diagram of the decomposition of the velocity of the refrigerant in the lower exhaust refrigerant passage hole.

[0044] Figure 11 is a top view Figure 1 When, the schematic diagram of the torque on the rotary valve.

[0045] Figure 12 is the schematic diagram of the functional relationship between the capacity and the rotational speed of a variable-frequency compressor when its rotational speed increases from low to high.

[0046] Figure 13 is the schematic diagram of the functional relationship between the capacity and the rotational speed of a variable-frequency compressor when its rotational speed decreases from high to low.

[0047] [Description of the attached drawing reference numerals is as follows]:

[0048] Intermediate plate - 1, First end face - 11, Second end face - 12, Lower exhaust refrigerant passage hole - 13, Groove - 14, First hole - 15, Rotary valve - 16, Flow guide vane - 17, Spring hole - 18, Spring - 19, Pusher - 110;

[0049] First cylinder - 2, Refrigerant passage hole - 21, Vane groove - 22, Air inlet - 23, First position - 24, Second position - 25;

[0050] Notch - 161, First plane - 162;

[0051] Front section of the cylinder - 3, Rear section of the cylinder - 4. Specific embodiments

[0052] To make the objectives, advantages and features of the present invention clearer, a variable-frequency compressor proposed by the present invention will be further described in detail below with reference to the accompanying drawings. It should be noted that the attached drawings are all in a very simplified form and use non-precise scales, only for conveniently and clearly assisting in explaining the objectives of the embodiments of the present invention.

[0053] In the description of the present invention, the limiting terms such as "first", "second", etc. are added for convenient description and reference, and cannot be understood as indicating or implying relative importance or implicitly specifying the quantity of the indicated technical features. Thus, the features limited by the limiting terms such as "first", "second", etc. may explicitly or implicitly include one or more of such features.

[0054] Such as Figures 1 to 9As shown in the figure, this embodiment provides a variable-frequency compressor, which includes an intermediate plate 1 and a first cylinder 2; the intermediate plate 1 includes a first end face 11 and a second end face 12, the first end face 11 is used to connect the first cylinder 2, and the second end face 12 is not communicated with the inner cavity of the first cylinder 2; a refrigerant passage hole 21 for refrigerant flow is provided on the cylinder wall of the first cylinder 2; the intermediate plate 1 is provided with a lower exhaust refrigerant passage hole 13, a groove 14, a first hole 15, a rotary valve 16, a guide vane 17, a spring hole 18, an elastic element and a push head 110; the lower exhaust refrigerant passage hole 13 is communicated with the refrigerant passage hole 21 on the first cylinder 2; the groove 14 is arranged on the first end face 11 of the intermediate plate 1, and the groove 14 penetrates the first end face 11 but does not penetrate the second end face 12; one end of the groove 14 is communicated with a first position 24 of the inner cavity of the first cylinder 2, and the other end is communicated with the first hole 15; the first hole 15 is communicated with a second position 25 of the inner cavity of the first cylinder 2; the orthographic projections of the first position 24 and the second position 25 on the first end face 11 do not coincide; the rotary valve 16 is installed in the first hole 15, the rotary valve 16 can rotate in the first hole 15, and the rotary valve 16 is hermetically connected with the first hole 15; the rotary valve 16 is provided with a notch 161, and the rotation of the rotary valve 16 is used to control the notch 161 to be in a communicating position or a closed position. When the notch 161 is in the communicating position, the other end of the groove 14, the notch 161 and the second position 25 are sequentially communicated. When the notch 161 is in the closed position, the notch 161 and the second position 25 are not communicated; the guide vane 17 is obliquely installed on the rotary valve 16, and the horizontal distance between the top of the guide vane 17 and the push head 110 is less than the horizontal distance between the bottom of the guide vane 17 and the push head 110; the guide vane 17 extends from the side of the rotary valve 16 into the lower exhaust refrigerant passage hole 13; the elastic element and the push head 110 are installed in the spring hole 18, the push head 110 abuts against the side of the rotary valve 16, the push head 110 is installed between the rotary valve 16 and the elastic element, and the elastic element is in a compressed state; the thrust of the push head 110 on the rotary valve 16 drives the notch 161 to be communicated with the second position 25.

[0055] Wherein, the elastic element can be a spring 19 or an elastic steel sheet. The first end face 11 and the second end face 12 of the intermediate plate 1 are usually arranged in parallel. When the first end face 11 is the upper end face, the second end face 12 is the lower end face, and the first cylinder 2 is the upper cylinder; when the first end face 11 is the lower end face, the second end face 12 is the upper end face, and the first cylinder 2 is the lower cylinder. In this embodiment, each of the following embodiments and the drawings mainly take the first end face 11 as the upper end face and the first cylinder 2 as the upper cylinder as an example for specific description. The lower exhaust refrigerant passage hole 13 and the refrigerant passage hole 21 are used to discharge the refrigerant at the bottom inside the housing of the variable frequency compressor to the top. The guide vane 17 is obliquely installed on the rotary valve 16. The refrigerant in the lower exhaust refrigerant passage hole 13 flows from bottom to top. When the rotational speed of the variable frequency compressor is greater than the critical speed, the guide vane 17 can overcome the elastic force of the elastic element under the action of the refrigerant thrust, so that the guide vane 17 drives the rotary valve 16 to rotate ( Figure 1 shown in the figure as a clockwise rotation), and the notch 161 on the rotary valve 16 can be changed from the communication position to the closed position.

[0056] The capacity of the variable frequency compressor provided in this embodiment can be changed. When the rotational speed of the variable frequency compressor is less than the critical speed, since the torque of the refrigerant thrust on the rotary valve 16 is less than the torque of the elastic element on the rotary valve 16, the notch 161 is in the communication position. During the rotation of the piston in the first cylinder 2, the gas between the first position 24 and the second position 25 in the inner cavity of the first cylinder 2 is not compressed. The volume of the gas compressed by the piston in one rotation decreases, the capacity of the variable frequency compressor decreases, the variable frequency compressor is in the small-capacity mode, the motor speed is relatively high, the efficiency is high, the oil return efficiency of the pump body is high, and the overall vibration is reduced, thereby improving the performance and reliability of the variable frequency compressor; when the rotational speed of the variable frequency compressor is greater than the critical speed, since the torque of the refrigerant thrust on the rotary valve 16 is greater than the torque of the elastic element on the rotary valve 16, the notch 161 is in the closed position, and the volume of the gas compressed by the piston in one rotation is equal to the volume of the gas compressed in the prior art, and the variable frequency compressor is in the full-capacity mode.

[0057] Optionally, as Figure 1 and Figure 5 shown, the lower exhaust refrigerant passage hole 13 intersects with the first hole 15. In this way, the width of the guide vane 17 can be designed to be shorter. The width of the guide vane refers to the dimension of the guide vane 17 in the horizontal direction. In other embodiments, the lower exhaust refrigerant passage hole 13 and the first hole 15 can be separated from each other, and a communication channel is provided between the lower exhaust refrigerant passage hole 13 and the first hole 15, but in this case, the width of the guide vane 17 is longer.

[0058] Optionally, as Figure 1 and Figure 4 shown, the first hole 15 penetrates through the first end face 11 and the second end face 12 of the intermediate plate 1, and the axis of the first hole 15 is parallel to the axis of the exhaust refrigerant passage hole 21. This facilitates the machining of the first hole 15.

[0059] Optionally, as Figure 1 and Figure 2 shown, the notch 161 on the rotary valve 16 is located at the top end of the rotary valve 16. This facilitates the machining of the notch 161. In other embodiments, the notch 161 may be located at a position between the top end and the bottom end of the rotary valve 16, as long as the notch 161 satisfies the following condition: when the rotational speed of the variable-frequency compressor is less than the critical speed, the other end of the groove 14, the notch 161, and the second position 25 are sequentially communicated; when the rotational speed of the variable-frequency compressor is greater than the critical speed, the notch 161 and the second position 25 are not communicated.

[0060] Optionally, the groove 14 is provided on the second end face of the intermediate plate 1, and the notch 161 is provided at the bottom of the rotary valve 16. When the variable-frequency compressor is placed vertically, the second end face of the intermediate plate 1 is the lower end face. By machining a groove 14 on the upper end face and the lower end face of the intermediate plate 1 respectively, a single rotary valve 16 can be used to adjust the capacities of the upper cylinder and the lower cylinder respectively.

[0061] Optionally, as Figure 5 and Figure 6 shown, the push head 110 includes a front end and a rear end. The shape of the front end is hemispherical, and the front end is in point contact with the side surface of the rotary valve 16; the shape of the rear end is cylindrical, and the rear end is connected to the elastic element. In this way, the sliding friction force between the rotary valve 16 and the push head 110 is small, and the rotary valve 16 can rotate smoothly.

[0062] Optionally, as Figure 2 and Figure 6 shown, the side surface of the rotary valve 16 includes a first plane 162 for contacting the front end of the push head 110. By machining a plane on the side surface of the rotary valve 16, it can be defined that the push head 110 contacts the rotary valve 16 on the first plane 162. The change in the position of the first plane 162 on the rotary valve 16 can change the direction of the force exerted by the push head 110 on the rotary valve 16, thereby changing the magnitude of the torque of the elastic element on the rotary valve 16.

[0063] Optionally, as Figures 6 to 9 shown and Figure 1As shown, the first cylinder 2 includes a vane groove 22 and an air inlet 23. The vane groove 22 and the air inlet 23 are on the orthographic projection of the first end face 11 of the intermediate plate 1. The line connecting the center of the vane groove 22 and the center of the lower exhaust refrigerant passage hole 13 is the first line, and the line connecting the center of the intermediate plate 1 and the center of the lower exhaust refrigerant passage hole 13 is the second line. The range of the included angle between the first line and the second line is between 0° and 20°. One end of the groove 14 intersects with one end of the air inlet 23 close to the inner cavity of the first cylinder 2.

[0064] In the solution provided in this embodiment, the lower exhaust refrigerant passage hole 13 can utilize the originally existing lower exhaust refrigerant passage hole 13 of the intermediate plate 1, or a new lower exhaust refrigerant passage hole 13 can be machined. The lower exhaust refrigerant passage hole 13 shown in the figure is the originally existing one of the intermediate plate 1. As Figure 6 and Figure 7 shown, when the compressor starts, under the action of the elastic element and the push head 110, the initial position of the rotary valve 16 is the communication position. The front section 3 of the cylinder (the front section of the cylinder refers to the position between the first position and the second position 25, that is, a section of the position straddled by the groove 14 and the first hole 15. Figure 6 In the figure, the front 3 sections of the cylinder are filled with horizontal lines, and the rear section 4 of the cylinder is filled with diagonal lines to distinguish these two regions) cannot form a seal, and the compression start angle is delayed. At this time, it is the low-capacity mode, and only the gas in the front section 3 of the cylinder can be compressed. As Figure 8 and Figure 9 shown, as the rotational speed increases, the refrigerant flow rate in the lower exhaust refrigerant passage hole 13 increases, and the force acting on the guide vane 17 increases. When its component force overcomes the moment of the elastic element push head 110, the rotary valve 16 rotates to the closed position, cutting off the groove 14 and the inner cavity of the cylinder. The compression start angle (the compression start angle is the position where the air inlet 23 is located) is restored. At this time, it is the full-capacity mode, and the gas in both the front section 3 and the rear section 4 of the cylinder can be compressed. As the exhaust gas flow rate of the lower cylinder increases, it can cause the refrigerant flow rate in the lower exhaust refrigerant passage hole 13 to increase, and the moment of the refrigerant on the rotary valve 16 further increases. The guide vane 17 abuts against the inner wall of the lower exhaust refrigerant passage hole 13, so that the rotary valve 16 is kept in the closed position.

[0065] Conversely, when the rotational speed decreases, the refrigerant flow rate in the lower exhaust refrigerant passage hole 13 decreases, and the refrigerant acting force decreases. When it is lower than the acting force of the elastic element, the rotary valve 16 returns to the initial position and switches back to the low-capacity mode.

[0066] When the included angle between the first connection line and the second connection line is equal to 0°, that is, when the second position 25 is directly opposite the blade, the capacity of the variable-frequency compressor is only half of the original capacity, so that the capacity of the variable-frequency compressor can be switched between the half-capacity mode and the full-capacity mode. When the second position 25 changes, the capacity of the variable-frequency compressor also changes accordingly. For example, when the second position 25 moves away from the air inlet 23, the capacity of the variable-frequency compressor is less than half-capacity.

[0067] The principle of the force received by the rotary valve 16 refers to Figures 6 to 13 as shown:

[0068] According to the law of conservation of momentum, mv = Ft, where m is the mass of the refrigerant, v is the flow velocity of the refrigerant, v can be decomposed into vx and vy, vx is perpendicular to the surface of the guide vane 17, vy is parallel to the surface of the guide vane 17, F is the force received by the guide vane 17, F can be decomposed into F piece and Fy, F piece is perpendicular to the surface of the guide vane 17, Fy is parallel to the surface of the guide vane 17, the included angle between F piece and F is θ, and t is the acting time of F.

[0069] m = ρV, where ρ is the density of the refrigerant and V is the volume of the refrigerant.

[0070] V = S * v * t, where S is the cross-sectional area of the lower exhaust refrigerant passage hole 13.

[0071] F piece = ρ * S * v 2 * cosθ

[0072] For example:

[0073] L spring = 0.003m (design size), F spring = 0.75N (design size)

[0074] When the torque of the elastic element is equal to the torque of the guide vane 17, F piece * L piece = F spring * L spring

[0075] L piece = 0.015m (design size)

[0076] Calculated F piece = 0.15N

[0077] S = 0.00005m 2 (design size)

[0078] Refer to Figure 12 As shown, according to the new national standard of R410A, the theoretical exhaust density ρ = 92 Kg / m 3(Calculation of the basic physical properties of the refrigerant, which changes with the refrigerant operating conditions), the velocity v = 5.7 m / s can be obtained. According to the flow velocity calculation program, the compressor speed in revolutions per minute (rpm) is approximately 3000. This is the critical point for half-capacity switching, that is, when the speed in the half-capacity mode increases to 3000 rpm, it can be switched to full capacity. 3000 rpm is the critical speed during the speed increase process. Refer to Figure 13 As shown, similarly, during deceleration, when the full-capacity mode decelerates to 1500 rpm, it switches to the half-capacity mode. 1500 rpm is the critical speed during the deceleration process. Figure 12 and Figure 13 The capacity in

[0079] Optionally, as Figure 1 shown, the shape of the intermediate plate 1 is an annular ring, and the first end face 11 and the second end face 12 of the intermediate plate 1 are parallel; the groove 14 includes a first part and a second part. The first part is one end of the groove 14, and the second part is the remaining part of the groove 14 after removing the first part. The shape of the second part is an arc, and the second part is located between the inner diameter and the outer diameter of the middle. This facilitates the design and machining of the groove 14.

[0080] Based on the same technical concept as the above-mentioned variable-frequency compressor, this embodiment provides another variable-frequency compressor, including an upper cylinder head and a second cylinder; the upper cylinder head includes a first end face 11 and a second end face 12, the first end face 11 is used to connect the second cylinder, and the second end face 12 is not communicated with the inner cavity of the second cylinder; a refrigerant passage hole for refrigerant flow is provided on the cylinder wall of the second cylinder; the upper cylinder head is provided with a lower exhaust refrigerant passage hole 13, a groove 14, a first hole 15, a rotary valve 16, a guide vane 17, a spring hole 18, an elastic element and a push head 110; the lower exhaust refrigerant passage hole 13 is communicated with the refrigerant passage hole on the second cylinder; the groove 14 is provided on the first end face 11 of the upper cylinder head, the groove 14 penetrates through the first end face 11 but does not penetrate through the second end face 12; one end of the groove is communicated with a first position 24 of the inner cavity of the second cylinder, and the other end is communicated with the first hole 15; the first hole 15 is communicated with a second position 25 of the inner cavity of the second cylinder; the orthographic projections of the first position 24 and the second position 25 on the first end face 11 do not coincide; the rotary valve 16 is installed in the first hole 15, the rotary valve 16 can rotate in the first hole 15, and the rotary valve 16 is hermetically connected with the first hole 15; the rotary valve 16 is provided with a notch 161, and the rotation of the rotary valve 16 is used to control the notch 161 to be in a communication position or a closed position. When the notch 161 is in the communication position, the other end of the groove, the notch 161 and the second position 25 are sequentially communicated. When the notch 161 is in the closed position, the notch 161 and the second position 25 are not communicated; the guide vane 17 is obliquely installed on the rotary valve 16, and the horizontal distance between the top of the guide vane 17 and the push head 110 is less than the horizontal distance between the bottom of the guide vane 17 and the push head 110; the guide vane 17 extends from the side of the rotary valve 16 into the lower exhaust refrigerant passage hole 13; the elastic element and the push head 110 are installed in the spring hole 18, the push head 110 abuts against the side of the rotary valve 16, the push head 110 is installed between the rotary valve 16 and the elastic element, and the elastic element is in a compressed state; the thrust of the push head 110 on the rotary valve 16 drives the notch 161 to be communicated with the second position 25. Among them, the variable-frequency compressor can be a single-cylinder compressor or a multi-cylinder compressor, and the second cylinder can be a single cylinder in the variable-frequency compressor or only the upper cylinder.

[0081] This embodiment has the same principle and function as the first embodiment, with the difference being that the lower exhaust refrigerant passage holes 13, grooves 14, first holes 15, rotary valves 16, guide vanes 17, spring holes 18, elastic elements, and push heads 110 are transferred from the intermediate plate 1 to the upper cylinder head. During specific use, since the intermediate plate 1 is relatively thick and is an annular flat plate, it is convenient to design and machine the relevant grooves and holes.

[0082] Based on the same technical concept as the above-mentioned variable-frequency compressor, referring to Figures 1 to 5 As shown, this embodiment provides another variable-frequency compressor, including a lower cylinder head and a third cylinder; the lower cylinder head includes a first end face 11 and a second end face 12, the first end face 11 is used to connect the third cylinder, and the second end face 12 is not communicated with the inner cavity of the third cylinder; a refrigerant passage hole for refrigerant flow is provided on the cylinder wall of the third cylinder; the lower cylinder head is provided with lower exhaust refrigerant passage holes 13, grooves, first holes 15, rotary valves 16, guide vanes 17, spring holes 18, elastic elements, and push heads; the lower exhaust refrigerant passage holes 13 are communicated with the refrigerant passage holes on the third cylinder; the groove is provided on the first end face 11 of the lower cylinder head, the groove penetrates the first end face 11 but does not penetrate the second end face 12; one end of the groove is communicated with a first position 24 in the inner cavity of the third cylinder, and the other end is communicated with the first hole 15; the first hole 15 is communicated with a second position 25 in the inner cavity of the third cylinder; the orthographic projections of the first position 24 and the second position 25 on the first end face 11 do not coincide; the rotary valve 16 is installed in the first hole 15, the rotary valve 16 is rotatable in the first hole 15, and the rotary valve 16 is hermetically connected to the first hole 15; the rotary valve 16 is provided with a notch 161, and the rotation of the rotary valve 16 is used to control the notch 161 to be in a communicating position or a closed position. When the notch 161 is in the communicating position, the other end of the groove, the notch 161, and the second position 25 are sequentially communicated. When the notch 161 is in the closed position, the notch 161 and the second position 25 are not communicated; the guide vane 17 is inclinedly installed on the rotary valve 16, and the horizontal distance between the top of the guide vane 17 and the push head is less than the horizontal distance between the bottom of the guide vane 17 and the push head; the guide vane 17 extends from the side of the rotary valve 16 into the lower exhaust refrigerant passage hole 13; the elastic element and the push head are installed in the spring hole 18, the push head abuts against the side of the rotary valve 16, the push head is installed between the rotary valve 16 and the elastic element, and the elastic element is in a compressed state; the thrust of the push head on the rotary valve 16 drives the notch 161 to communicate with the second position 25. Among them, the variable-frequency compressor can be a single-cylinder compressor or a multi-cylinder compressor, and the third cylinder can be a single cylinder or only the lower cylinder in the variable-frequency compressor.

[0083] The principle and function of this embodiment are the same as those of the first embodiment. The differences are as follows: the lower exhaust refrigerant passage holes 13, grooves 14, first holes 15, rotary valves 16, guide vanes 17, spring holes 18, elastic elements and push heads 110 are transferred from the intermediate plate 1 to the lower cylinder head.

[0084] In summary, the capacity of a variable-frequency compressor provided by the present invention can be changed. When the rotational speed of the variable-frequency compressor is less than the critical speed, since the torque of the refrigerant thrust on the rotary valve 16 is less than the torque of the elastic element on the rotary valve 16, the notch 161 is in the communication position. During the rotation of the piston in the first cylinder 2, the gas between the first position 24 and the second position 25 in the inner cavity of the first cylinder 2 is not compressed. The volume of the gas compressed by the piston in one revolution decreases, the capacity of the variable-frequency compressor decreases, the variable-frequency compressor is in the small-capacity mode, the motor speed is relatively high, the efficiency is high, the oil return efficiency of the pump body is high, and the overall vibration is reduced, thereby improving the performance and reliability of the variable-frequency compressor; when the rotational speed of the variable-frequency compressor is greater than the critical speed, since the torque of the refrigerant thrust on the rotary valve 16 is greater than the torque of the elastic element on the rotary valve 16, the notch 161 is in the closed position, and the volume of the gas compressed by the piston in one revolution is equal to the volume of the gas compressed in the prior art, and the variable-frequency compressor is in the full-capacity mode.

[0085] The above description is only a description of the preferred embodiments of the present invention, and does not limit the scope of the present invention in any way. Any changes and modifications made by those of ordinary skill in the art according to the above disclosure belong to the protection scope of the present invention.

Claims

1. A variable-frequency compressor, characterized in that, It includes an intermediate plate and a first cylinder; the intermediate plate includes a first end face and a second end face, the first end face is used to connect the first cylinder, and the second end face is not communicated with the inner cavity of the first cylinder; a refrigerant passage hole for refrigerant flow is provided on the cylinder wall of the first cylinder; The intermediate plate is provided with a lower exhaust refrigerant passage hole, a groove, a first hole, a rotary valve, a guide vane, a spring hole, an elastic element and a push head; The lower exhaust refrigerant passage hole is communicated with the refrigerant passage hole on the first cylinder; The groove is arranged on the first end face of the intermediate plate, the groove penetrates through the first end face but does not penetrate through the second end face; one end of the groove is communicated with a first position of the inner cavity of the first cylinder, and the other end is communicated with the first hole; the first hole is communicated with a second position of the inner cavity of the first cylinder; the orthographic projections of the first position and the second position on the first end face do not coincide; The rotary valve is installed in the first hole, the rotary valve can rotate in the first hole, and the rotary valve is hermetically connected with the first hole; the rotary valve is provided with a notch, and the rotation of the rotary valve is used to control the notch to be in a communicating position or a closed position. When the notch is in the communicating position, the other end of the groove, the notch and the second position are sequentially communicated. When the notch is in the closed position, the notch and the second position are not communicated; The guide vane is obliquely installed on the rotary valve, the side of the guide vane close to the first end face approaches the direction of the push head, and the side of the guide vane close to the second end face moves away from the direction of the push head; the guide vane extends from the side surface of the rotary valve into the lower exhaust refrigerant passage hole; The elastic element and the push head are installed in the spring hole, the push head abuts against the side surface of the rotary valve, the push head is installed between the rotary valve and the elastic element, and the elastic element is in a compressed state; The thrust of the push head on the rotary valve drives the notch to be communicated with the second position; The lower exhaust refrigerant passage hole intersects with the first hole; The first hole penetrates through the first end face and the second end face, and the axis of the first hole is parallel to the axis of the lower exhaust refrigerant passage hole.

2. A variable frequency compressor according to claim 1, characterized in that, The first cylinder includes a vane groove and an air inlet. In the orthographic projection of the vane groove and the air inlet on the first end face of the intermediate plate, the connecting line between the center of the vane groove and the center of the lower exhaust refrigerant passage hole is the first connecting line, and the connecting line between the center of the intermediate plate and the center of the lower exhaust refrigerant passage hole is the second connecting line. The range of the included angle between the first connecting line and the second connecting line is between 0° and 20°. One end of the groove intersects with the end of the air inlet close to the inner cavity of the first cylinder.

3. A variable-frequency compressor according to claim 1, characterized in that, The shape of the intermediate plate is annular, and the first end face and the second end face of the intermediate plate are parallel; the groove includes a first part and a second part. The first part is one end of the groove, and the second part is the remaining part of the groove after removing the first part. The shape of the second part is arc-shaped, and the second part is located between the inner diameter and the outer diameter of the intermediate plate.

4. A variable frequency compressor according to claim 1, characterized in that, The notch on the rotary valve is located at the top end of the rotary valve.

5. A variable frequency compressor according to claim 1, characterized in that, The push head includes a front end and a rear end. The shape of the front end is hemispherical, and the front end is in point contact with the side surface of the rotary valve; the shape of the rear end is cylindrical, and the rear end is connected to the elastic element.

6. A variable-frequency compressor according to claim 5, characterized in that, The side surface of the rotary valve includes a first plane for contacting the front end of the push head.

7. A variable frequency compressor, characterized in that, It includes an upper cylinder head and a second cylinder; the upper cylinder head includes a first end face and a second end face. The first end face is used to connect the second cylinder, and the second end face is not communicated with the inner cavity of the second cylinder; a refrigerant passage hole for refrigerant flow is provided on the cylinder wall of the second cylinder; The upper cylinder head is provided with a lower exhaust refrigerant passage hole, a groove, a first hole, a rotary valve, a guide vane, a spring hole, an elastic element and a push head; The lower exhaust refrigerant passage hole is communicated with the refrigerant passage hole on the second cylinder. The groove is provided on the first end face of the upper cylinder head. The groove penetrates the first end face but does not penetrate the second end face; one end of the groove is communicated with a first position of the inner cavity of the second cylinder, and the other end is communicated with the first hole; the first hole is communicated with a second position of the inner cavity of the second cylinder; the orthographic projections of the first position and the second position on the first end face do not coincide; The rotary valve is installed in the first hole. The rotary valve can rotate in the first hole, and the rotary valve is hermetically connected with the first hole; the rotary valve is provided with a notch. The rotation of the rotary valve is used to control the notch to be in a communicating position or a closed position. When the notch is in the communicating position, the other end of the groove, the notch and the second position are sequentially communicated. When the notch is in the closed position, the notch and the second position are not communicated; The guide vane is obliquely installed on the rotary valve. The side of the guide vane close to the first end face approaches the direction of the push head, and the side of the guide vane close to the second end face moves away from the direction of the push head; the guide vane extends from the side surface of the rotary valve into the lower exhaust refrigerant passage hole; The elastic element and the push head are installed in the spring hole. The push head abuts against the side surface of the rotary valve. The push head is installed between the rotary valve and the elastic element, and the elastic element is in a compressed state; The thrust of the push head on the rotary valve drives the notch to communicate with the second position; The lower exhaust refrigerant passage hole intersects with the first hole. The first hole penetrates the first end face and the second end face, and the axis of the first hole is parallel to the axis of the lower exhaust refrigerant passage hole.

8. A variable frequency compressor, characterized in that, It includes a lower cylinder head and a third cylinder; the lower cylinder head includes a first end face and a second end face. The first end face is used to connect the third cylinder, and the second end face is not communicated with the inner cavity of the third cylinder; a refrigerant passage hole for refrigerant flow is provided on the cylinder wall of the third cylinder; The lower cylinder head is provided with a lower exhaust refrigerant passage hole, a groove, a first hole, a rotary valve, a guide vane, a spring hole, an elastic element and a push head; The lower exhaust refrigerant passage hole is communicated with the refrigerant passage hole on the third cylinder. The groove is provided on the first end face of the lower cylinder head, and the groove penetrates the first end face but does not penetrate the second end face; one end of the groove communicates with the first position of the inner cavity of the third cylinder, and the other end communicates with the first hole; the first hole communicates with the second position of the inner cavity of the third cylinder; the orthographic projections of the first position and the second position on the first end face do not coincide; The rotary valve is installed in the first hole, the rotary valve is rotatable in the first hole, and the rotary valve is sealingly connected with the first hole; the rotary valve is provided with a notch, and the rotation of the rotary valve is used to control the notch to be in a communicating position or a closed position. When the notch is in the communicating position, the other end of the groove, the notch and the second position are sequentially communicated. When the notch is in the closed position, the notch and the second position are not communicated; The guide vane is obliquely installed on the rotary valve. The side of the guide vane close to the first end face approaches the direction of the push head, and the side of the guide vane close to the second end face moves away from the direction of the push head; the guide vane extends from the side of the rotary valve into the lower exhaust refrigerant passage hole; The elastic element and the push head are installed in the spring hole, the push head abuts against the side of the rotary valve, the push head is installed between the rotary valve and the elastic element, and the elastic element is in a compressed state; The thrust of the push head on the rotary valve drives the notch to communicate with the second position; The lower exhaust refrigerant passage hole intersects with the first hole; The first hole penetrates the first end face and the second end face, and the axis of the first hole is parallel to the axis of the lower exhaust refrigerant passage hole.

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