Capacity-controlled rotary compressor and refrigeration cycle device

Abstract

The present invention discloses a capacity-controlled rotary compressor, wherein the compressor structure, driven by an electric motor and equipped with low-pressure gas absorption means and high-pressure gas discharge means, comprises: a cylinder having a compression chamber, two component parts respectively connected to the planes on both sides of the cylinder, a vane groove opening in the compression chamber, a vane having a rectangular cross-section that slides between the vane groove and the two component parts, and a vane back cavity that closes the vane back in the vane groove; on either side of the sliding surface of the vane and the vane groove, or on either side of the sliding surface of the vane and the two component parts, a high-pressure groove is formed on one sliding surface, and high-low pressure grooves connected to the vane back cavity are formed on the other sliding surface. The capacity-controlled rotary compressor has a variable capacity function, and the vane has low sliding loss and wear.

Description

Technical Field

[0001] The present invention relates to the field of refrigeration technology, and in particular to a capacity-controlled rotary compressor and a refrigeration cycle device. Background Art

[0002] Rotary compressor capacity control involves switching the compressor's effective displacement (refrigeration capacity) between two to four modes by stopping and starting the vanes in motion. This, combined with variable-frequency motor speed control, allows for a balanced air conditioning experience with both comfort and energy efficiency (APF).

[0003] To expand the application of this technology to air conditioners, it is necessary to improve the reliability of the vane's stationary and de-stationary operation. This means ensuring responsiveness to capacity control under high and low pressure fluctuations and eliminating vane sliding losses during capacity control, thus requiring long-term response reliability. However, existing variable capacity compressors experience constant vane sliding friction, resulting in energy loss and vane groove wear. Summary of the Invention

[0004] The present invention aims to solve at least one of the technical problems existing in the prior art.

[0005] Therefore, an object of the present invention is to provide a capacity-controlled rotary compressor having a variable capacity function and low sliding loss and wear of a sliding vane.

[0006] The present invention also provides a refrigeration cycle device with a capacity-controlled rotary compressor.

[0007] The cam is pressurized and presses on the cam surface to release oil, and the cam surface is pressurized to release oil, so that the cam surface is compressed and the cam surface is kept clean and the cam surface is kept in a state of emergency.

[0008] According to the embodiment of the present invention, the capacity-controlled rotary compressor has a variable capacity function and has small sliding loss and wear of the sliding vane.

[0009] In some embodiments, the high-low pressure connecting groove connecting the aforementioned sliding vane back cavity and the aforementioned high-low pressure groove is provided on the aforementioned sliding vane or the aforementioned sliding surface.

[0010] In some embodiments, the two aforementioned components refer to a bearing that is fitted with a sliding clearance on the crankshaft driven by the aforementioned electric motor, and an intermediate plate that is engaged with the aforementioned cylinder; or any one of the two aforementioned bearings or the two aforementioned intermediate plates.

[0011] In some embodiments, the high-pressure tank is in communication with the exhaust muffler on the compressor structure.

[0012] In some embodiments, the compressor structure is provided with at least two compression chambers, and at least one of the compression chambers is provided with a sliding vane stationary means and a stationary release means.

[0013] According to some embodiments of the present invention, a capacity-controlled rotary compressor includes: a shell; a compressor structure, which is arranged in the shell, and the compressor structure includes: a cylinder, two element parts arranged on two sides of the cylinder, and a vane, the cylinder has a vane groove, the vane can slide in the vane groove, the vane has an upper and a lower surface, and the two element parts have sliding surfaces that slide with the upper and lower surfaces; a high- and low-pressure groove is provided on the sliding surface of one of the element parts, and a high-pressure groove is provided on the sliding surface of the other element part, the high- and low-pressure grooves are suitable for connecting high-pressure pressure or low-pressure pressure, the vane is stationary when the high- and low-pressure grooves are connected to the low-pressure pressure, and the vane is released from stationary when the high- and low-pressure grooves are connected to the high-pressure pressure.

[0014] In some embodiments, the cylinder has a vane back cavity suitable for connecting high pressure and low pressure, and the element component provided with the high and low pressure grooves is also provided with high and low pressure connecting grooves, and the high and low pressure connecting grooves are connected with the high and low pressure grooves and the vane back cavity.

[0015] In some embodiments, the high-pressure groove and the high- and low-pressure grooves are opposite to each other in the height direction of the slide, and the component component provided with the high-pressure groove is also provided with a high-pressure hole, and the high-pressure hole connects the high-pressure groove and the muffler provided on the component component.

[0016] According to an embodiment of the present invention, a capacity-controlled rotary compressor includes a shell; a compressor structure, which is arranged in the shell, and the compressor structure includes: a cylinder and a vane, the cylinder has a vane groove, the vane can slide in the vane groove, the vane has a first side surface and a second side surface, the first side surface is provided with a high-low pressure groove, the second side surface is provided with a high-pressure groove, the high-low pressure groove is suitable for connecting high pressure or low pressure, the vane is stationary when the high-low pressure groove is connected to the low pressure, and the vane is released from stationary when the high-low pressure groove is connected to the high pressure.

[0017] In some embodiments, the high-pressure groove and the high-low pressure grooves are directly opposite to each other in the thickness direction of the sliding vane.

[0018] In some embodiments, the high-pressure groove and the high-low pressure grooves are both circular, and the centers of the circles are opposite in the thickness direction and have the same radii.

[0019] In some embodiments, the cylinder has a vane back cavity suitable for connecting high pressure and low pressure, a high and low pressure connecting groove connecting the vane back cavity and the high and low pressure grooves is provided on the first side, and a high pressure gas groove connected to the high pressure groove is provided on the second side, and the high pressure gas groove is suitable for connecting high pressure.

[0020] In some embodiments, the high-pressure gas groove is perpendicular to the high- and low-pressure connecting grooves.

[0021] In some embodiments, the center of the high-pressure groove and the centers of the high- and low-pressure grooves are both located on a side of the longitudinal center of the sliding vane close to the sliding vane back cavity.

[0022] According to an embodiment of the present invention, a capacity-controlled rotary compressor includes: a shell; a compressor structure, wherein the compressor structure is arranged in the shell, and the compressor structure includes: a cylinder and a vane, wherein the cylinder has a vane groove, and the vane can slide in the vane groove, and the vane groove has two sliding surfaces that cooperate with the vane, wherein a high- and low-pressure groove is provided on the sliding surface of one of the vane grooves and a high-pressure groove is provided on the sliding surface of the other vane groove, and the high- and low-pressure grooves are suitable for connecting high-pressure pressure or low-pressure pressure, and the vane is stationary when the high- and low-pressure grooves are connected to the low-pressure pressure, and the vane is released from stationary when the high- and low-pressure grooves are connected to the high-pressure pressure.

[0023] In some embodiments, the cylinder has a slide back cavity suitable for connecting high pressure and low pressure, and a high-low pressure connecting groove connecting the slide back cavity and the high-low pressure groove is provided on the first side of the slide, and a high-pressure gas groove connected to the high-pressure groove is provided on the second side of the slide, and the high-pressure gas groove is suitable for connecting high pressure.

[0024] In some embodiments, the radial inner end of the high- and low-pressure connecting groove corresponds to the high- and low-pressure grooves to connect the high- and low-pressure grooves, and the outer end of the high- and low-pressure connecting groove is connected to the back cavity of the slide; the upper end of the high-pressure gas groove corresponds to the high-pressure groove to connect the high-pressure groove, and the lower end of the high-pressure gas groove is suitable for connecting high-pressure pressure.

[0025] In some embodiments, the high-pressure groove and the high-low pressure grooves are opposite to each other in the thickness direction of the sliding vane, and the high-pressure groove and the high-low pressure grooves are both circular, with the centers of the circles facing each other in the thickness direction and the radii being equal.

[0026] The refrigeration cycle device according to the embodiment of the present invention includes the capacity-controlled rotary compressor, the condenser, the expansion device, the evaporator of the above embodiment, and a switching means between high pressure and low pressure.

[0027] Technical effects of the present invention:

[0028] 1) Through the action of high and low pressure grooves and high pressure grooves, the slide can be easily stopped and released, with simple switching and fast response;

[0029] 2) The extrusion pressure required to stop and release the slide can be easily set;

[0030] 3) Because the side pressure of the sliding vane during operation is 0 or close to 0 due to capacity control, there will be no energy loss and wear problems;

[0031] 4) By increasing the vane static force, capacity control of large rotary compressors becomes possible.

[0032] Additional aspects and advantages of the present invention will be set forth in part in the description which follows and, in part, will be obvious from the description which follows, or may be learned by practice of the present invention. BRIEF DESCRIPTION OF THE DRAWINGS

[0033] The above and / or additional aspects and advantages of the present invention will become apparent and readily understood from the following description of the embodiments with reference to the accompanying drawings, in which:

[0034] Figure 1 is a schematic diagram of a compressor according to an embodiment of the present invention;

[0035] Figure 2 yes Figure 1 A partial enlarged view of an embodiment;

[0036] Figure 3 yes Figure 1 A perspective view of a slide according to an embodiment;

[0037] Figure 4 yes Figure 1A schematic diagram of a slide of an embodiment;

[0038] Figure 5 It is along Figure 4 Schematic diagram of the X-section;

[0039] Figure 6 It is along Figure 4 Schematic diagram of the Y section;

[0040] Figure 7 is a schematic diagram of releasing the slide;

[0041] Figure 8 is a schematic diagram of a compressor according to another embodiment;

[0042] Figure 9 yes Figure 8 A perspective view of a slide according to an embodiment;

[0043] Figure 10 It is along Figure 8 Schematic diagram of the Z section;

[0044] Figure 11 is a schematic diagram of a compressor according to another embodiment;

[0045] Figure 12 yes Figure 11 A central cross-sectional plan view of a cylinder of an embodiment;

[0046] Figure 13 yes Figure 11 A perspective view of a slide according to an embodiment;

[0047] Figure 14 yes Figure 11 A partial schematic diagram of a slide of an embodiment;

[0048] Figure 15 yes Figure 11 A schematic diagram of a stationary slide of an embodiment;

[0049] Figure 16 yes Figure 11 Schematic diagram of the sliding plate being released from rest according to an embodiment. DETAILED DESCRIPTION

[0050] The following describes embodiments of the present invention in detail. Examples of the embodiments are shown in the accompanying drawings, wherein the same or similar reference numerals throughout represent the same or similar elements or elements having the same or similar functions. The embodiments described below with reference to the accompanying drawings are exemplary and are intended only to explain the present invention and are not to be construed as limiting the present invention.

[0051] Implementation Status 1:

[0052] Figure 1The illustration shows a two-cylinder capacity-controlled rotary compressor 80 and the refrigeration cycle system of an air conditioner connected to this compressor 80. The two-cylinder capacity-controlled rotary compressor 80 primarily consists of an inverter-operated electric motor 4 fixed to the inner periphery of a sealed housing 2, and a compressor structure 5 driven by the electric motor 4 and having a capacity-controlled function. Lubricating oil 6 is sealed at the bottom of the housing 2.

[0053] The compressor structure 5 is composed of the A cylinder 10, the B cylinder 20, the intermediate partition 16 connected between the two planes, the main bearing 45 connected to the upper side of the A cylinder 10, the auxiliary bearing 47 connected to the lower side of the B cylinder 20, the crankshaft 40 slidingly fitted between the two bearings, and the mufflers 46a and 47b respectively provided on the main bearing 45 and the auxiliary bearing 47. These essential parts are connected by a plurality of bolts 7 ( Figure 2 ) assembly, the outer periphery of cylinder A 10 is fixed on the inner periphery of the shell 2.

[0054] The A-suction pipe 11 is connected to the side of the A-cylinder 10, the B-suction pipe 21 and the pressure conversion pipe 26 are connected to the side of the B-cylinder 20, and the high-pressure pipe 2a is connected to the side of the housing 2. The high-pressure pipe 2a, the pressure conversion pipe 26, and the B-suction pipe 21 are connected to a three-way valve 50. The three-way valve 50 switches the pressure in the B-slide back chamber 25, described later, between high and low pressure.

[0055] During operation of compressor structure 5, cylinder B 20 is the capacity-controlled cylinder, while cylinder A 10 is the cylinder in constant operation. Through the operation of cylinders A 10 and B 20, high-pressure gas, which has been absorbed and compressed in their respective compression chambers, is discharged into muffler 46a and muffler 47b, respectively.

[0056] The high-pressure gas discharged into the muffler 47b flows through the vent hole 48 and merges with the muffler 46a. After being discharged from the muffler discharge hole 46b to the space below the electric motor 4, it is discharged from the discharge pipe 3 through the electric motor 4 to the four-way valve 60 of the refrigeration cycle. In addition, although the discharge pressure is low for several tens of seconds after the compressor structure 5 starts operating, the pressure in the muffler 46a and the muffler 47b is slightly higher than the internal pressure of the casing 2 due to the large discharge flow rate.

[0057] The high-pressure gas discharged through the four-way valve 60 to the indoor heat exchanger 61 is condensed and reduced to low pressure by passing through the expansion device 62. After evaporating in the outdoor heat exchanger 63, it again passes through the four-way valve 60 and the accumulator 65 and returns to the A intake pipe 11 and the B intake pipe 21, where it is absorbed by the A cylinder 10 and the B cylinder 20, respectively. While the above is a heating cycle, switching the gas flow path through the four-way valve 60 changes the cycle to a cooling cycle.

[0058] Figure 2It is a cross-sectional view of the compressor structure 5, showing its internal structure and the connection between the three pipes and the three-way valve 50. Figure 3 This is the slide vane 30 used in the first embodiment, and is the same as the A slide vane 13 applied to the A cylinder 10 in the first embodiment. Figure 4 An enlarged view of the B cylinder 20 is shown. Figure 5 and Figure 6 The floor plans show Figure 4 In the X-section and Y-section of FIG. 1 , in these figures, the B slide 30 is in a stationary state.

[0059] exist Figure 2 In the diagram, cylinder A 10 and cylinder B 20 are equipped with rolling piston A 12 and rolling piston B 22, respectively, which are driven by crankshaft 40. Slide plate A 13, equipped with slide plate spring 14, abuts against rolling piston A 12, reciprocating therewith. Slide plate B 30 is in an operationally stationary state. Therefore, cylinder B 20 is in a "cylinder-off" state. "Cylinder-off" refers to a state in which rolling piston B 22 is not in contact with slide plate B 30 and is idling.

[0060] The main bearing 45 and the auxiliary bearing 47 each have exhaust holes 45a and 47a, respectively. The upper end of the A-slide back cavity 15 on the back of the operating A-slide 13 opens into the housing 2. Therefore, the A-slide back cavity 15 is constantly under high pressure during operation of the compressor structure 5. Meanwhile, the B-slide back cavity 25 on the back of the stationary B-slide 30 is sealed at both ends by the middle diaphragm 16 and the auxiliary bearing 47, respectively. The back of the B-slide back cavity 25 is connected to the pressure switching pipe 26.

[0061] The high-pressure inlet pipe 50a of the three-way valve 50, located outside the housing 2, is connected to the high-pressure pipe 2a formed in the housing 2. The low-pressure inlet pipe 50b is connected to the B suction pipe 21, and the outlet pipe 51 is connected to the pressure switching pipe 26. The pressure switching pipe 26 is connected to the back cavity 25 of the B slide.

[0062] Because the slide valve 52 moves left and right to open and close the output pipe 51 through the microcomputer control of the air conditioner, the pressure of the output pipe 51 can be freely switched between low pressure (the pressure of the B suction pipe 21) and high pressure (the pressure of the shell 2). Figure 2 state) and high voltage.

[0063] Figure 3 The B slide 30 used in embodiment 1 is shown, which has the same shape as the A slide 13. The semicircular front end 32 abuts against the outer periphery of the B rolling piston 22 in the compression operation state, and the B slide 30 does not abut in the static cylinder operation.

[0064] The cross-sectional shape of the B slide 30 is a rectangle, and the A side 30a (i.e., the first side 30a) and the B side 30b (i.e., the second side 30b) are aligned with the B slide groove 24 ( Figure 5 ) sliding plane. Symbol W is the width of the slide. The upper surface 30c and the lower surface 30d slide on the lower surface of the middle partition 16 and the upper surface of the auxiliary bearing 47, respectively.

[0065] Figure 4 and showing X and Y sections Figure 5 and Figure 6 In the embodiment, there is a high and low pressure groove 18b processed under the middle partition 16 on which the upper side 30c of the B slide 30 slides, and a high and low pressure connecting groove 18c connected to the groove and opened at the upper end of the B slide back cavity 25.

[0066] On the upper surface of the auxiliary bearing 47, which slides on the lower surface 30d of the B slide 30, the high-pressure groove 18a, located opposite the high- and low-pressure grooves 18b, is connected to the high-pressure port 49 formed in the muffler 47b. Furthermore, the high- and low-pressure connecting groove 18c is common to all embodiments of the present invention.

[0067] Figure 4 The symbol Fa on the stationary B vane 30 indicates that during operation of the compressor structure 5, the B vane 30 is constantly affected by the pressure difference between the high-pressure groove 18a (high pressure (Pd)) and the high-low-pressure groove 18b (low pressure (Ps)) connected to the back cavity 25 of the B vane. This pressure difference causes the B vane 30 to be stationary beneath the middle diaphragm 16 due to the squeezing pressure of Fa. The shapes of the high-pressure groove 18a and the high-low-pressure groove 18b are not limited to circular; for example, they may be elliptical.

[0068] The width W of the B slide 30 ( Figure 3 ) When the output power of the compressor is 1-2HP (applied to household air conditioners), it is about 3mm, and when it is 3-5HP, it is 4-5mm. In implementation state 1, when the extrusion pressure Fa acts on a part of this width W, the B slide 30 is stationary.

[0069] Because the forces acting on the rear end 33 and the front end 32 of the B slide 30 are both equal low pressures (Ps), normally, if the extrusion pressure Fa>0.2 kgF (2 N), the B slide 30 stops and remains stationary.

[0070] Figure 5 Shown are the high- and low-pressure grooves 18b and the high- and low-pressure connecting grooves 18c, which connect to the back chamber of slide B, on the center diaphragm 16. These grooves are located in the center of the top surface 30c of slide B 30. Because of the high- and low-pressure connecting grooves 18c, the pressures in the high- and low-pressure grooves 18b and back chamber 25 of slide B are equal, regardless of whether slide B 30 is operating or stationary.

[0071] That is, if the pressure switching tube 26 is at low pressure (Ps), the high-low pressure tank 18b is also at low pressure; if the pressure switching tube 26 is at high pressure (Pd), the high-low pressure tank 18b is also at high pressure. Furthermore, the pressure switching of the pressure switching tube 26 causes the pressure in the high-low pressure tank 18b to switch instantly.

[0072] Figure 6 Shown are the high-pressure groove 18a and high-pressure hole 49 machined into the auxiliary bearing 47. Because the high-pressure hole 49 is formed in the muffler 46a and communicates with the interior of the muffler 46a, the pressure in the high-pressure groove 18a rises and becomes high pressure when the compressor assembly 5 starts operating. Thereafter, the pressure remains high until the compressor assembly 5 stops operating. By forming the high-pressure hole 49 in the muffler 46a, it is possible to easily stop the B vane 30 within 10 seconds after the compressor assembly 5 starts operating.

[0073] Figure 7 The illustration shows the moment during operation of the compressor structure 5 when the pressure switching pipe 26, the B vane back chamber 25, the high- and low-pressure connecting grooves 18c, and the high- and low-pressure grooves 18b are switched to high pressure (Pd) by the switching of the three-way valve 50. Because the high-pressure groove 18a, which is opposite the high- and low-pressure grooves 18b, is at high pressure (Pd), the vane pressing force Fa mentioned above becomes zero.

[0074] When the B vane 30 is opened, the high pressure in the back chamber 25 of the B vane causes the tip of the B vane 30 to abut against the outer circumference of the orbiting B rolling piston 22, initiating compression of the B compression chamber 20a. This effectively releases the cylinder deactivation mechanism. Since the A cylinder 10 is operating, two cylinders are now operating, improving refrigeration capacity. Furthermore, since the extrusion pressure Fa is zero during the operation of the B vane 30, energy loss and wear losses due to capacity control are eliminated.

[0075] Subsequently, when the pressure switching line is switched to low pressure via three-way valve 50, high-low pressure groove 18a switches to low pressure. As a result, the B vane 30 is stationary in B vane groove 24 due to the vane extrusion pressure Fa. In other words, cylinder B 20 begins to operate in a deactivated state, achieving capacity control during operation.

[0076] Although the difference ΔP between the high pressure (Pd) and the low pressure (Ps) is small within 10 seconds after the compressor structure 5 begins operating, the pressure in the back chamber 25 of the B vane is set to the high pressure under this condition, Fa = 0, allowing the B vane 30 to be easily started. Thus, implementation state 1 has the advantage of clear and rapid response when starting and stopping the B vane 30.

[0077] This effect is not only effective during normal operation, but also reduces defrost time during heating operation. Conversely, the strong static force of vane B can also be applied to capacity control of large multi-cylinder rotary compressors exceeding 5 HP. Furthermore, since implementation 1 does not require the processing of special parts or additional components, it offers manufacturing cost advantages.

[0078] In the above-mentioned embodiment 1, the middle partition 16 and the auxiliary bearing 47 are respectively provided with a high-pressure groove 18a, a high-low pressure groove 18b and a high-low pressure connecting groove 18c. The effect is the same when they are installed on the upper and lower sides of the B slide 30c 30d.

[0079] Figure 1 or Figure 2 In the capacity-controlled rotary compressor with two cylinders, cylinder A and cylinder B, the two essential components connected to the two side planes of cylinder B are the auxiliary bearing 47 and the middle partition 16. In the capacity-controlled rotary compressor composed of one cylinder, the above two essential components are the main bearing 45 and the auxiliary bearing 47. In the capacity-controlled rotary compressor composed of three cylinders, the above two essential components are the two middle partitions 16.

[0080] Implementation Status 2:

[0081] Figure 8 The diagram shows a longitudinal plan view of the structure of the compressor structure 5 in embodiment 2. As in embodiment 1, the A slide 13 provided on the A cylinder 10 is in motion, and the B slide 30 provided on the B cylinder 20 is stationary.

[0082] Figure 9 In the B-slide 30 shown in FIG, side A 30a (i.e., first side 30a) and side A 30b (i.e., second side 30b) are provided with opposing high- and low-pressure grooves 18b and high-pressure groove 18a, respectively. High- and low-pressure connecting groove 18c is connected to high- and low-pressure grooves 18b and is opened in the back cavity 25 of the B-slide. Meanwhile, high-pressure gas groove 19 is connected to high-pressure groove 18a, and high-pressure gas groove 19 is connected to high-pressure hole 49 in the auxiliary bearing 47.

[0083] Figure 10 yes Figure 8 The Z-end view shows the center plane view of cylinder B 20. Slide B 30, stationary in slide B slot 24, is located in the opposing high-pressure groove 18a and high-low-pressure groove 18b. High-pressure groove 18a is always at high pressure. One side of high-low-pressure groove 18b is connected to the low-pressure back chamber 25 of slide B via a high-low-pressure connecting groove 18c, maintaining low pressure. Therefore, the extrusion pressure Fa acts on the side of slide B 30, which remains stationary in slide B slot 24.

[0084] Afterwards, if Figure 11As shown, if the back chamber 25 of the B vane is switched to high pressure due to the control of the three-way valve 50, the extrusion pressure Fa returns to 0 and the B vane 30 is activated. Therefore, the compressor structure 5 is operated in two cylinders.

[0085] During the operation of the B-slide 30, the high-pressure gas groove 19 does not need to constantly be open to the high-pressure hole 49. For example, when the B-slide 30 reaches a certain stage or position in its movement, the B-slide 30 can be connected to the high-pressure gas groove 19. If the high-pressure gas groove 19 and the high-pressure hole 49 are designed to be connected at the top dead center or bottom dead center of the slide 30, where the slide 30 momentarily stops during its operation, the high pressure in the high-pressure gas groove 19 can be fully maintained. This is because at the top dead center or bottom dead center, the reciprocating speed of the B-slide 30 is zero, and the supply of high-pressure gas to the high-pressure groove 18a is not hindered.

[0086] The depth of high-pressure groove 18a and high-low pressure groove 18b is 0.2-0.4mm, which is sufficient. The four grooves on B slide 30 can be stamped. Furthermore, slides are typically tumbled during final processing, which is ideal for chamfering the grooves.

[0087] The positioning of the high-pressure groove 18a and the high-low-pressure groove 18b prevents the side loads caused by the maximum stroke of the B slide 30 in the B compression chamber 20. Therefore, regardless of the length of operation, the two side grooves will not wear. In other words, it is best to place the two grooves slightly behind the center of the side of the B slide 30.

[0088] Let's try calculating the extrusion pressure Fa. When vane B 30 is stationary, assume that the combined diameters of the high-pressure groove (high pressure (Pd)) and the high-low pressure groove 18b (low pressure (Ps)) are 4 mm (area A = approximately 0.5 cm²). Furthermore, assuming the refrigerant used in the most popular air conditioner is R410A, and that the high-pressure side pressure (Pd) is 3.1 MPa and the low-pressure side pressure (Ps) is 1.0 MPa during relatively high-load operation, Fa ≈ 3.7 kgf (37 N).

[0089] That is, if the B-slide back cavity 25 is at low pressure (Ps), the B-slide 30 will rest on the side of the B-slide groove 24 under a side pressure of 3.7 kgf. Needless to say, the value of Fa should be optimized by adjusting the areas of the high-pressure groove 18a and the high-low pressure groove 18b.

[0090] For reference, under the aforementioned pressure conditions, the B slider 30 is released from its stationary position by the control of the three-way valve 50, and Fa = 0. The extrusion pressure Fb at the rear end of the B slider 30, caused by the high pressure (Pd) in the B slider back chamber 25, is approximately 18 kgf. In this calculation, the width and height of the B slider 30 are 3 mm and 20 mm, respectively.

[0091] If it is set according to the condition that the back cavity 25 of the B slide is at high pressure before the compressor in the stopped state starts to run, since Fb > Fa after the compressor starts to run, the B slide 30 usually starts to run automatically within five seconds. If the back cavity 25 of the slide before starting to run is set to low pressure, since Fb < Fa = 0, the B slide 30 continues to be stationary.

[0092] Implementation state 3:

[0093] Figure 12 The plan view of the central section of the B cylinder 20 is shown. In the figure, the design is to equip the high-pressure grooves 18a and the high-low pressure grooves 18b on both sliding surfaces of the sliding surface of the B slide groove 24. Figure 13 The high-pressure gas groove 19 and the high-low pressure connection groove 18c on the B slide 30 are shown. The high-pressure groove 18a is connected to the high-pressure hole 49 of the auxiliary bearing 47, and the high-low pressure groove 18b is connected to the high-low pressure connection groove 18c and communicates with the back cavity 25 of the B slide.

[0094] Figure 14 The high-pressure groove 18a installed on one side surface of the B slide groove 24 of the B cylinder 20 is shown. As described above, the high-pressure groove 18a is connected to the high-pressure hole 49 via the high-pressure gas groove 19 installed on the side surface of the B slide 30.

[0095] Figure 15 The high-pressure groove 18a and the high-low pressure groove 18b on the sliding surface of the B slide groove 24 opposite to it are shown. The high-pressure groove 18a is connected to the high-pressure hole 49 via the high-pressure gas groove 19 on the B slide 30. The high-low pressure groove 18b is connected to the back cavity 25 of the B slide via the high-low pressure connection groove 18c on the B slide 30.

[0096] Figure 16 The reciprocating motion state in which the back cavity 25 of the B slide becomes high pressure through the control of the three-way valve 50, the stationary state of the B slide 30 is released, and it abuts against the B rolling piston 22 is shown. Thus, the implementation state 3 shows the design of arranging the high-pressure groove 18a and the high-low pressure groove 18b on the B slide groove 24 and arranging the high-pressure gas groove 19 and the high-low pressure connection groove 18c connected to them on the B slide 30. The functions and effects of the implementation state 3 are similar to those of the implementation state 2

[0097] In Figure 1-Figure 7 In the embodiment of, the capacity control type rotary compressor 80 includes a housing 2 and a compressor structural part 5.

[0098] The compressor structure 5 is arranged in the shell 2, and the compressor structure 5 includes: a cylinder 20 (i.e., B cylinder 20), two element components 16, 47 (such as the middle partition 16 and the auxiliary bearing 47) arranged on the two sides of the cylinder 20, and a slide 30 (i.e., B slide 30), the cylinder 20 has a slide groove 24, the slide 30 can slide in the slide groove 24, the slide 30 has an upper surface 30c and a lower surface 30d, and the two element components 16, 47 have sliding surfaces that slide with the upper surface 30c and the lower surface 30d.

[0099] A high- and low-pressure groove 18b is provided on the sliding surface of one of the element parts, such as the middle partition 16, and a high-pressure groove 18a is provided on the sliding surface of another element part, such as the auxiliary bearing 47. The high- and low-pressure groove 18b is suitable for connecting high pressure or low pressure. When the high- and low-pressure groove 18b is connected to low pressure, the sliding vane 30 is stationary, and when the high- and low-pressure groove 18b is connected to high pressure, the sliding vane 30 is released from stationary state.

[0100] like Figure 1-Figure 7 In the embodiment shown, the cylinder 20 has a vane back cavity 25 suitable for connecting high pressure and low pressure, and the element parts provided with high and low pressure grooves 18b, such as the middle partition 16, are also provided with high and low pressure connecting grooves 18c, and the high and low pressure connecting grooves 18c are connected with the high and low pressure grooves 18b and the vane back cavity 25.

[0101] like Figure 1-Figure 7 In the embodiment shown, the high-pressure groove 18a and the high-low pressure groove 18b are directly opposite to each other in the height direction of the slide 30, and the component part provided with the high-pressure groove 18a, such as the auxiliary bearing 47, is also provided with a high-pressure hole 49. The high-pressure hole 49 connects the high-pressure groove 18a and the muffler 47b provided on the component part.

[0102] exist Figures 8-10 In the embodiment, the capacity-controlled rotary compressor 80 includes a housing 2 and a compressor structure 5 .

[0103] The compressor structure 5 is arranged in the shell 1, and the compressor structure 5 includes: a cylinder 20 (i.e., B cylinder 20) and a vane 30 (i.e., B vane 30), the cylinder 20 has a vane groove 24, the vane 30 can slide in the vane groove 24, the vane 30 has a first side surface 30a and a second side surface 30b, the first side surface 30a is provided with a high-pressure groove 18b, and the second side surface 30b is provided with a high-pressure groove 18a, the high-pressure groove 18b is suitable for connecting high pressure or low pressure, when the high-pressure groove 18b is connected to low pressure, the vane 30 is stationary, and when the high-pressure groove 18b is connected to high pressure, the vane 30 is released from the stationary state.

[0104] exist Figures 8-10 In the embodiment of the present invention, the high-pressure groove 18a and the high-low pressure groove 18b are opposite to each other in the thickness direction of the sliding vane 30. As a result, the forces on both sides of the sliding vane 30 are more evenly distributed.

[0105] exist Figures 8-10 In the embodiment, the high-pressure groove 18a and the high-low-pressure groove 18b are both circular, with the centers of the circles facing each other in the thickness direction and the radii being equal.

[0106] exist Figures 8-10 In the embodiment, the cylinder 20 has a vane back cavity 25 suitable for connecting high pressure and low pressure, and a high-low pressure connecting groove 18c connecting the vane back cavity 25 and the high-low pressure groove 18b is provided on the first side 30a, and a high-pressure gas groove 19 connected to the high-pressure groove 18a is provided on the second side 30b, and the high-pressure gas groove 19 is suitable for connecting high pressure.

[0107] exist Figures 8-10 In the embodiment, the high-pressure gas groove 19 is perpendicular to the high-low pressure connection groove 18c. That is, the high-pressure gas groove 19 is staggered, for example, vertically arranged, so that the strength of the sliding vane 30 is not significantly reduced by the multiple grooves, thereby increasing the life of the sliding vane 30.

[0108] exist Figures 8-10 In the embodiment, the center of the high-pressure groove 18a and the center of the high-low pressure groove 18b are both located on the side of the longitudinal center (center in the length direction) of the slide 30 close to the slide back cavity 25 (ie, the rear side).

[0109] like Figures 11-16 As shown, the capacity-controlled rotary compressor 80 includes a housing 2 and a compressor structure 5 .

[0110] The compressor structure 5 is arranged in the shell 2, and the compressor structure 5 includes: a cylinder 20 (i.e., B cylinder 20) and a vane 30 (B vane 30). The cylinder 20 has a vane groove 24, and the vane 30 can slide in the vane groove 24. The vane groove 24 has two sliding surfaces that cooperate with the vane 30. A high-low pressure groove 18b is provided on one of the sliding surfaces of the vane groove 24, and a high-pressure groove 18a is provided on the other sliding surface of the vane groove 24. The high-low pressure groove 18b is suitable for connecting high pressure or low pressure. When the high-low pressure groove 18b is connected to the low pressure, the vane 30 is stationary, and when the high-low pressure groove 18b is connected to the high pressure, the vane 30 is released from the stationary state.

[0111] like Figures 11-16 As shown, the cylinder 20 has a slide back cavity 24 suitable for connecting high pressure and low pressure, and a high-low pressure connecting groove 18c connecting the slide back cavity 25 and the high-low pressure groove 18b is provided on the first side 30a of the slide 30. A high-pressure gas groove 19 connected to the high-pressure groove 18a is provided on the second side 30b of the slide 30, and the high-pressure gas groove 19 is suitable for connecting high pressure.

[0112] like Figures 11-16As shown, the radial inner end of the high-low pressure connecting groove 18b corresponds to the high-low pressure groove 18b, thereby connecting the high-low pressure groove 18b, and the outer end of the high-low pressure connecting groove 18c is connected to the slide back cavity 25; the upper end of the high-pressure gas groove 19 corresponds to the high-pressure groove 18a, thereby connecting the high-pressure groove 18a, and the lower end of the high-pressure gas groove 19 is suitable for connecting high pressure.

[0113] Throughout this specification, reference to terms such as "one embodiment," "some embodiments," "illustrative embodiments," "examples," "specific examples," or "some examples" means that a specific feature, structure, material, or characteristic described in conjunction with that embodiment or example is included in at least one embodiment or example of the present invention. In this specification, illustrative uses of the above terms do not necessarily refer to the same embodiment or example. Furthermore, the specific features, structures, materials, or characteristics described may be combined in any suitable manner in any one or more embodiments or examples.

[0114] While embodiments of the present invention have been shown and described, it will be appreciated by those skilled in the art that various changes, modifications, substitutions, and variations may be made to the embodiments without departing from the principles and spirit of the invention, and that the scope of the invention is defined by the claims and their equivalents.

Claims

1. A capacity-controlled rotary compressor, characterized in that: The compressor structure, which is driven by an electric motor and has low-pressure gas absorption means and high-pressure gas discharge means, comprises: a cylinder having a compression chamber, two component parts respectively connected to the flat surfaces on both sides of the cylinder, a sliding vane groove with a hole opening in the compression chamber, a sliding vane having a rectangular cross-section that slides between the sliding vane groove and the two component parts, a sliding vane back cavity that closes the back of the sliding vane in the sliding vane groove, and a muffler provided on the component parts; On either side of the sliding surface of the vane and the vane groove, or on either side of the sliding surface of the vane and the two element components, a high-pressure groove is formed on one sliding surface, and a high-low pressure groove is formed on the other sliding surface connected to the vane back cavity; if the pressure in the vane back cavity is low, the vane is stationary in the vane groove; if the pressure in the vane back cavity is high, the vane is released from its stationary state and abuts against a rolling piston orbiting in the compression cavity; The high-pressure tank is connected to the muffler through a high-pressure hole, and the high-pressure hole penetrates the component part in which the muffler is installed; A high-low pressure connection groove connecting the aforementioned sliding vane back cavity and the aforementioned high-low pressure groove is provided on the aforementioned sliding vane or the aforementioned sliding surface.

2. The capacity-controlled rotary compressor according to claim 1, wherein: The two aforementioned components are a bearing that is fitted with a sliding clearance on the crankshaft driven by the electric motor, and an intermediate plate that is engaged with the cylinder; or either of the two aforementioned bearings or the two aforementioned intermediate plates.

3. The capacity-controlled rotary compressor according to claim 1, wherein: The high-pressure tank is in communication with the exhaust muffler on the compressor structure.

4. The capacity-controlled rotary compressor according to claim 1, wherein: The compressor structure is provided with at least two compression chambers, and at least one of the compression chambers is provided with a vane stationary means and a stationary release means.

5. A capacity-controlled rotary compressor, characterized in that: include: case; A compressor structure, the compressor structure being disposed within the housing and comprising: a cylinder, two element components disposed on two sides of the cylinder, and a vane, the cylinder having a vane groove, the vane being slidable within the vane groove, the vane having an upper surface and a lower surface, the two element components having sliding surfaces slidably engaged with the upper surface and the lower surface; A high- and low-pressure groove is provided on the sliding surface of one of the element parts, and a high-pressure groove is provided on the sliding surface of the other element part, wherein the high- and low-pressure grooves are adapted to communicate with high pressure or low pressure, and the sliding vane is stationary when the high- and low-pressure grooves communicate with the low pressure, and the sliding vane is released from stationary state when the high- and low-pressure grooves communicate with the high pressure; The high-pressure groove and the high-low pressure groove are directly opposite to each other in the height direction of the sliding vane, and the element component provided with the high-pressure groove is further provided with a high-pressure hole, the high-pressure hole communicating with the high-pressure groove and the muffler provided on the element component, and the high-pressure hole penetrates the element component; The cylinder has a vane back cavity suitable for connecting high pressure and low pressure. The element component provided with the high and low pressure grooves is also provided with high and low pressure connecting grooves, and the high and low pressure connecting grooves are connected with the high and low pressure grooves and the vane back cavity.

6. A capacity-controlled rotary compressor, characterized in that: include: case; A compressor structure, the compressor structure is arranged in the housing, and the compressor structure includes: a cylinder and a vane, the cylinder having a vane groove, the vane being slidable in the vane groove, the vane having a first side surface and a second side surface, the first side surface being provided with a high- and low-pressure groove, the second side surface being provided with a high-pressure groove, the high- and low-pressure grooves being adapted to communicate with high-pressure pressure or low-pressure pressure, the vane being stationary when the high- and low-pressure grooves are connected to the low-pressure pressure, and the vane being released from stationary state when the high- and low-pressure grooves are connected to the high-pressure pressure; The compressor structure further includes a secondary bearing provided below the cylinder and a muffler provided on the secondary bearing, the high-pressure groove is connected to the muffler via a high-pressure hole, and the high-pressure hole passes through the secondary bearing; The cylinder has a vane back cavity suitable for connecting high pressure and low pressure, and a high-low pressure connecting groove connecting the vane back cavity and the high-low pressure groove is provided on the first side. A high-pressure gas groove connected to the high-pressure groove is provided on the second side, and the high-pressure gas groove is suitable for connecting high pressure; the high-pressure gas groove is perpendicular to the high-low pressure connecting groove.

7. The capacity-controlled rotary compressor according to claim 6, wherein: The high-pressure groove and the high-low-pressure groove are directly opposite to each other in the thickness direction of the sliding vane.

8. The capacity-controlled rotary compressor according to claim 7, wherein: The high-pressure groove and the high-low pressure grooves are both circular, with the centers of the circles facing each other in the thickness direction and the radii being equal.

9. The capacity-controlled rotary compressor according to claim 6, wherein: The center of the high-pressure groove and the centers of the high- and low-pressure grooves are both located on one side of the longitudinal center of the sliding vane close to the sliding vane back cavity.

10. A capacity-controlled rotary compressor, characterized in that: include: case; A compressor structure, the compressor structure is arranged in the shell, the compressor structure includes: a cylinder and a vane, the cylinder has a vane groove, the vane can slide in the vane groove, the vane groove has two sliding surfaces that cooperate with the vane, a high-low pressure groove is provided on the sliding surface of one of the vane grooves and a high-pressure groove is provided on the sliding surface of the other vane groove, the high-low pressure grooves are suitable for connecting high-pressure pressure or low-pressure pressure, the vane is stationary when the high-low pressure grooves are connected to the low-pressure pressure, and the vane is released from stationary when the high-low pressure grooves are connected to the high-pressure pressure; the compressor structure also includes a sub-bearing arranged below the cylinder and a muffler arranged on the sub-bearing, the high-pressure groove is connected to the muffler through a high-pressure hole, and the high-pressure hole passes through the sub-bearing; The cylinder has a slide back cavity suitable for connecting high pressure and low pressure, a high and low pressure connecting groove connecting the slide back cavity and the high and low pressure grooves is provided on the first side of the slide, and a high pressure gas groove connected to the high pressure groove is provided on the second side of the slide, and the high pressure gas groove is suitable for connecting high pressure.

11. The capacity-controlled rotary compressor according to claim 10, wherein: The radial inner end of the high- and low-pressure connecting groove corresponds to the high- and low-pressure grooves, thereby connecting the high- and low-pressure grooves, and the outer end of the high- and low-pressure connecting groove is connected to the back cavity of the slide; the upper end of the high-pressure gas groove corresponds to the high-pressure groove, thereby connecting the high-pressure groove, and the lower end of the high-pressure gas groove is suitable for connecting high-pressure pressure.

12. The capacity-controlled rotary compressor according to claim 10, wherein: The high-pressure groove and the high-low pressure grooves are opposite to each other in the thickness direction of the sliding vane. The high-pressure groove and the high-low pressure grooves are both circular, with the centers of the circles facing each other in the thickness direction and the radii being equal.

13. A refrigeration cycle device comprising the capacity-controlled rotary compressor according to any one of claims 1 to 12, a condenser, an expansion device, an evaporator, and a means for switching between high pressure and low pressure.

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