WO2016179813A1 - 旋转式压缩机及具有其的冷冻装置 - Google Patents

旋转式压缩机及具有其的冷冻装置 Download PDF

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Publication number
WO2016179813A1
WO2016179813A1 PCT/CN2015/078868 CN2015078868W WO2016179813A1 WO 2016179813 A1 WO2016179813 A1 WO 2016179813A1 CN 2015078868 W CN2015078868 W CN 2015078868W WO 2016179813 A1 WO2016179813 A1 WO 2016179813A1
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WIPO (PCT)
Prior art keywords
valve
rotary compressor
exhaust
cylinder
chamber
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PCT/CN2015/078868
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English (en)
French (fr)
Inventor
小津政雄
向卫民
喻继江
张�诚
巫华龙
王玲
钟亮
闫丽丽
Original Assignee
广东美芝制冷设备有限公司
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Application filed by 广东美芝制冷设备有限公司 filed Critical 广东美芝制冷设备有限公司
Priority to PCT/CN2015/078868 priority Critical patent/WO2016179813A1/zh
Publication of WO2016179813A1 publication Critical patent/WO2016179813A1/zh

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/04—Heating; Cooling; Heat insulation

Definitions

  • the present invention relates to the field of refrigeration, and more particularly to a rotary compressor and a refrigeration apparatus therewith.
  • a liquid refrigerant injection for preventing overheating of the rotary compressor or a gas refrigerant injection method for improving the heating capacity has been popularized. They can also be used as a lubricant recovery technology that recycles lubricating oil into a compressor. On the other hand, it is required to improve the efficiency of these fluid injection devices, and to improve the design and manufacturability.
  • the present invention aims to solve at least one of the technical problems in the related art to some extent.
  • the present invention proposes a rotary compressor which has a simple structure, improves fluid injection efficiency, and improves versatility and manufacturability.
  • the present invention also proposes a refrigeration apparatus having the above rotary compressor.
  • a rotary compressor includes a sealed casing, a compression mechanism portion, and a fluid injection device, the compression mechanism portion being housed in the casing, the compression mechanism portion including at least one cylinder, a main bearing, a secondary bearing, a crankshaft, a piston and a vane, each of the cylinders having a compression chamber open to the opposite two cylinder planes, the piston being eccentrically operated in the compression chamber, the crankshaft driving the piston to operate eccentrically
  • the main bearing and the sub-bearing slidably support the crankshaft, and the sliding piece reciprocates synchronously with the piston; each of the compression chambers corresponds to one of the fluid injection devices, and each of the fluid injection devices
  • the utility model comprises: a valve cavity opening to any of the cylinder planes of the compression chamber; an exhaust hole opening to the valve cavity; an exhaust valve of a plate for opening the exhaust hole; and the valve cavity and the An exhaust passage opening the compression chamber; a refrigerant or lubricating oil injection circuit communicating with the
  • the opening or closing of the vent hole is realized by using the pressure fluctuation of the compression chamber, the configuration of the fluid injection device is simple, the fluid injection efficiency and reliability are high, and the versatility and manufacturability are improved.
  • the cylinders are two, and a middle partition is disposed between the two cylinders.
  • the valve chamber is provided with a leaf spring or a coil spring that presses the exhaust valve to the exhaust hole side.
  • the cylinder is one, at the cylinder plane, and the cylinder plane is connected
  • the valve chamber is disposed between one of the main bearings or the sub-bearings, and the other side has a groove opposite to the valve chamber.
  • the valve chamber is disposed between the cylinder plane and the main bearing, the sub-bearing or the intermediate partition connecting the cylinder plane, and the other side is provided There is a recess opposite the valve cavity.
  • the exhaust passage is eccentrically disposed with the exhaust hole.
  • the difference between the minimum inner circumference of the valve chamber and the maximum outer circumference of the exhaust valve is in the range of 0.01 to 0.2 mm.
  • the sliding piece is provided with a slit groove, and the slit groove changes the opening length in the compression chamber by the reciprocating motion of the sliding piece, the exhaust passage and the exhaust passage
  • the valve chamber is in communication with the slit groove.
  • the shape of the exhaust valve is circular or polygonal.
  • a freezing apparatus includes the rotary compressor according to the above embodiment of the present invention.
  • Figure 1 is a longitudinal sectional view showing the inside of a rotary compressor in connection with Embodiment 1 of the present invention
  • Figure 2 is a cross-sectional view taken along line X-X of Figure 1, showing a plan view of a refrigerant injection device in a cylinder plane;
  • Figure 3 is a detailed cross-sectional view of the refrigerant injection device associated with the first embodiment
  • Embodiment 4 is related to Embodiment 1, and is a detailed plan view of the refrigerant injection device;
  • Figure 5 is a structural diagram of the refrigerant injection device, relating to the first embodiment
  • Figure 6 is related to the first embodiment, showing a design example of the valve chamber and the flow of the refrigerant
  • Figure 7 is a longitudinal sectional view of the main bearing equipped with a refrigerant injection device in connection with the first embodiment
  • Figure 8 is related to the first embodiment, showing that the main bearing is provided with a groove
  • Figure 9 is a longitudinal sectional view showing a refrigerant injection device in a middle partition of a two-cylinder rotary compressor according to a second embodiment of the present invention.
  • Figure 10 is a plan view showing a refrigerant injection device in which a slit groove is provided in a slider according to Embodiment 3 of the present invention.
  • Figure 11 is related to the third embodiment and is a detailed view of the sliding slot of the slider;
  • Figure 12 is a view showing a practical example in which lubricating oil is injected into a compression chamber in connection with Embodiment 4 of the present invention.
  • Rotary compressor 1 housing 2, motor 3, oil pool 8,
  • Compression mechanism portion 4 cylinders 30 (30a, 30b), rolling piston 78, slide 75, crankshaft 70, main bearing 50, sub-bearing 60, cylinder plane 32a (32b), compression chamber vent 34, exhaust muffler 65, the sliding groove 35, the groove 52, the slit groove 75a, the suction hole 7,
  • Fluid injection device 10 (10a, 10b), valve chamber 12, vent hole 11, exhaust valve 20, leaf spring 21, exhaust passage 15, refrigerant passage 16, valve seat 12a,
  • a compression chamber 31 a low pressure chamber 33b, a high pressure chamber 33a,
  • a refrigerant injection pipe 40 an exhaust pipe 5, a condenser 80, an expansion valve 81, an evaporator 82, a suction pipe 6, a refrigerant injection circuit 85, an oil separator 83,
  • a two-cylinder rotary compressor 90 and a middle partition 55 A two-cylinder rotary compressor 90 and a middle partition 55.
  • first and second are used for descriptive purposes only and are not to be construed as indicating or implying a relative importance or implicitly indicating the number of technical features indicated.
  • features defining “first” or “second” may include at least one of the features, either explicitly or implicitly.
  • the meaning of "a plurality” is at least two, such as two, three, etc., unless specifically defined otherwise.
  • the terms “installation”, “connected”, “connected”, “fixed” and the like shall be understood broadly, and may be either a fixed connection or a detachable connection, unless explicitly stated and defined otherwise. Or in one piece; it may be a mechanical connection, or it may be an electrical connection or a communication with each other; it may be directly connected or indirectly connected through an intermediate medium, and may be an internal connection of two elements or an interaction relationship between two elements. Unless otherwise expressly defined. For those skilled in the art, the specific meanings of the above terms in the present invention can be understood on a case-by-case basis.
  • a rotary compressor according to an embodiment of the present invention will be described in detail with reference to FIGS. 1 to 12, wherein the rotary compressor may be a vertical compressor, a horizontal compressor, a rocking rotary compressor, and a housing low-pressure rotary type. Compressor, two-cylinder compressor or two-stage compression compressor.
  • the rotary compressor can be applied to a refrigerating device which further includes components such as a condenser 80, an evaporator 82, and an expansion valve 81.
  • a rotary compressor includes a sealed casing 2, a compression mechanism portion 4, and a fluid injection device 10.
  • the compression mechanism portion 4 is housed in a casing 2, and the compression mechanism portion 4 includes at least one cylinder and a main bearing. 50. a secondary bearing 60, a crankshaft 70, a piston 78 and a vane 75, each cylinder having a compression chamber 31 open to the opposite two cylinder planes,
  • the piston 78 is eccentrically operated in the compression chamber 31, the crankshaft 70 drives the piston 78 to operate eccentrically, the main bearing 50 and the sub-bearing 60 slidably support the crankshaft 70, and the slider 75 reciprocates in synchronization with the piston 78.
  • the main bearing 50 and the sub-bearing 60 are respectively disposed on the two cylinder planes of the cylinder.
  • the cylinders are two, and a middle partition 55 is disposed between the two cylinders.
  • the main bearing 50, the sub-bearing 60 and the intermediate partition 55 are respectively disposed at the cylinder planes of the two cylinders. on.
  • Each compression chamber 31 corresponds to a fluid injection device 10, and each fluid injection device 10 includes a valve chamber 12 that is open to any of the cylinder planes of the compression chamber 31.
  • a venting opening 11 that opens to the valve chamber 12.
  • the exhaust valve 20 of the flat plate that opens and closes the vent hole 11.
  • a refrigerant or lubricating oil that communicates with the vent hole 11 is injected into the circuit 85.
  • the venting opening 11 is synchronized with the eccentric operation of the piston 78.
  • the refrigerant or lubricating oil injection circuit 85 can be connected between the condenser 80 and the expansion valve 81, the pressure of the refrigerant or lubricating oil injection circuit 85 is lower than the pressure of the condenser 80, and the pressure of the evaporator 82 is higher than that of the evaporator 82 to form a refrigerant injection.
  • Pressure (Pi) The exhaust valve 20 is used to open the exhaust hole 11, the exhaust passage 15 communicates with the compression chamber 31 and the valve chamber 12, and the refrigerant or lubricating oil injection circuit 85 communicates with the exhaust hole 11, and during the eccentric operation of the piston 78, the compression chamber 31 The pressure changes, so there is a pressure difference between the two sides of the exhaust valve 20.
  • the exhaust valve 20 opens the exhaust hole 11 from the refrigerant or lubrication.
  • the refrigerant or lubricating oil flowing in the oil injection circuit 85 flows into the compression chamber 31 through the exhaust hole 11 and the exhaust passage 15.
  • the exhaust valve 20 closes the vent hole 11. Thereby, the exhaust valve 20 opens and closes the exhaust hole 11 in accordance with the pressure change of the compression chamber 31.
  • the fluid injection device 10 can be disposed on the cylinder or on the main bearing 50 or the sub-bearing 60.
  • the fluid injection device 10 is provided.
  • the fluid injection device 10 is provided on the main bearing 50.
  • each cylinder corresponds to one fluid injection device 10, and the fluid injection device 10 corresponding to each cylinder may be disposed in the corresponding cylinder, the intermediate partition 55, the corresponding main bearing 50 or the auxiliary bearing 60 of the cylinder. Any one of them.
  • the two fluid injection devices 10 share a refrigerant or lubricating oil injection circuit 85, and the two fluid injection devices 10 are disposed on the intermediate partition 55.
  • the opening or closing of the exhaust hole 11 is realized by the pressure variation of the compression chamber 31, the configuration of the fluid injection device 10 is simple, the fluid injection efficiency and reliability are high, and the versatility is improved. Manufacturability.
  • the valve chamber 12 is provided with a leaf spring 21 or a coil spring that presses the exhaust valve 20 against the exhaust hole 11 side. Thereby, it is ensured that the exhaust valve 20 can close the exhaust hole 11.
  • the cylinder is one, between the cylinder plane, and the main bearing 50 or the sub-bearing 60 connecting the cylinder plane, one side is provided with a valve chamber 12, and the other side has a groove opposite to the valve chamber 12. 52. That is, you can One of the valve chamber 12 and the recess 52 is disposed on the cylinder, and the other of the valve chamber 12 and the recess 52 is disposed on the main bearing 50 or the sub-bearing 60, and the valve chamber 12 and the recess 52 are disposed opposite each other.
  • the stroke of the gas valve 20 is maximum, by providing the groove 52, the high pressure environment in the groove 52 can ensure that the exhaust valve 20 can close the vent hole 11.
  • valve chamber 12 there are two cylinders, between the cylinder plane, and the main bearing 50, the sub-bearing 60 or the intermediate partition 55 connecting the cylinder plane, one side is provided with a valve chamber 12, and the other is provided with a valve
  • the cavity 12 is opposite the groove 52. That is, one of the valve chamber 12 and the recess 52 may be provided on the cylinder, and the valve chamber 12 and the recess 52 may be disposed in the intermediate partition 55, the main bearing 50 or the sub-bearing 60 corresponding to the cylinder. another.
  • the stroke of the exhaust valve 20 is maximized, by providing the recess 52, the high pressure environment within the recess 52 ensures that the exhaust valve 20 can close the venting opening 11.
  • the exhaust passage 15 is eccentrically disposed with the venting opening 11.
  • the difference between the minimum inner circumference of the valve chamber 12 and the maximum outer circumference of the exhaust valve 20 is in the range of 0.01 to 0.2 mm. Thereby, it is ensured that the exhaust valve 20 can smoothly move up and down within the valve chamber 12.
  • the slider 75 is provided with a slit groove 75a.
  • the slit groove 75a changes the opening length in the compression chamber 31, and exhausts
  • the passage 15 communicates with the valve chamber 12 and the slit groove 75a. Therefore, it is possible to prevent the refrigerant or the lubricating oil flowing in from the refrigerant or the lubricating oil injection circuit 85 from entering the suction hole 7, ensuring the amount of the refrigerant sucked from the suction hole 7, and ensuring the refrigeration capacity of the rotary compressor.
  • the exhaust valve 20 has a circular or polygonal shape.
  • a freezing apparatus includes the rotary compressor according to the above embodiment of the present invention.
  • the rotary compressor 1 is composed of a compression mechanism portion 4 fixed to the inner circumference of the casing 2 and an electric motor 3 disposed on the upper portion thereof.
  • the compression mechanism unit 4 is a rolling piston 78 that is eccentrically rotated in a cylindrical compression chamber provided in the cylinder 30, and a slide 75 (shown in FIG. 2) that reciprocates synchronously with the rolling piston 78 to make a rolling
  • the piston 78 is eccentrically rotated by a crankshaft 70, a main bearing 50 that slidably supports the crankshaft 70, and a main bearing 60.
  • the main bearing 50 on the cylinder plane 32a and the sub-bearing 60 on the cylinder plane 32b are respectively connected by five screws.
  • a compression chamber exhaust hole 34 and an exhaust muffler 65 are provided in the sub-bearing 60.
  • the embodiment 1 is a circular valve chamber 12 that is open to the cylinder flat surface 32a, an exhaust hole 11 that opens the center opening, an exhaust valve 20 that opens and closes the exhaust hole 11, and the exhaust valve 20 is arranged in a row.
  • the leaf spring 21 pressed by the air hole 11 and the exhaust passage 15 that communicates the valve chamber 12 and the compression chamber 31 are composed.
  • a form composed of these elements is referred to as a fluid injection device 10.
  • the vent hole 11 opens a hole in the refrigerant passage 16, and a cold connection to the outer side of the casing 2 is connected in the refrigerant passage 16.
  • the medium is injected into the tube 40.
  • the condenser 80 of the refrigeration cycle connected to the exhaust pipe 5 (FIG. 12) provided at the upper end of the casing 2 is connected to the expansion valve 81 and the evaporator 82, and the outlet of the evaporator 82 is connected to a suction pipe fixed to the casing 2. 6.
  • a refrigerant injection circuit 85 connected between the condenser 80 and the expansion valve 81 is connected to the refrigerant injection pipe 40.
  • the refrigerant that has passed through the refrigerant injection circuit 85 is additionally connected to the capillary (not shown) or the gas-liquid separator (not shown) due to the resistance of the circuit or the refrigerant injection circuit 85.
  • the pressure is reduced by means of other means. Therefore, the pressure of the refrigerant injection pipe 40 is lower than the pressure of the condenser 80, and is higher than the pressure of the evaporator 82, and the refrigerant injection pressure (Pi) is formed.
  • Fig. 2 is a plan view showing the X-X cross section of Fig. 1;
  • the fluid injection device 10 provided in the cylinder plane 32a, the piping connecting the cylinders 30, and the inside of the compression chamber 31 are shown.
  • the cylinder 30 constituting the compression mechanism portion 4 has a cylindrical compression chamber in the center thereof, and a circular valve chamber 12 is opened to the cylinder flat surface 32a of the opening surface thereof, and a vent hole 11 and a valve seat 12a are provided at the center thereof.
  • the suction pipe 6 is connected to the side of the compression chamber 31.
  • the exhaust valve 20 and the leaf spring 21 accommodated in the valve chamber 12 for opening and closing the discharge port 11 are not shown.
  • the rolling piston 78 which is driven to rotate eccentrically in the counterclockwise direction by the crankshaft 70, and the sliding plate 75 which is slidably abutted against the outer circumference thereof divides the compression chamber 31 into a low pressure chamber 33b connecting the suction pipe 6 and a high pressure chamber connecting the exhaust passage 15. 33a.
  • the pressure of the valve chamber 12 at each revolution of the rolling piston 78 varies between a low pressure equal to the suction pressure and a high pressure equal to the discharge pressure.
  • FIG. 3 is a detailed cross-sectional view of the fluid injection device 10 shown in Fig. 1.
  • 4 is a plan view of the fluid injection device 10
  • FIG. 5 is a structural view of the fluid injection device 10.
  • the circular valve chamber 12 which is open to the fluid injection device 10 provided in the cylinder plane 32a of Fig. 3, is a circular groove machined on the cylinder plane 32a, and that open end is connected to the plane of the main bearing 50.
  • the exhaust passage 15 opens a hole in the valve chamber 12 and the compression chamber 31.
  • the disk-shaped leaf spring 21 of the outer periphery thereof is pressed on the exhaust valve 20, and the vertical movement of the exhaust valve 20 is stabilized by the spring effect thereof, and the exhaust valve is made when the high-pressure refrigerant of the compression chamber 31 flows back to the valve chamber 12 20 quickly returned.
  • the inner diameter (d) of the valve chamber 12 is approximately 8 to 12 mm, and the height of the valve seat 12a is 1.5 to 3 mm.
  • the thickness of the exhaust valve 20 installed in the valve chamber 12 is in the range of 0.1 to 0.3 mm, and the outer diameter thereof is smaller than the inner diameter (d) of the valve chamber 12, and the difference is 0.01 to 0.2 mm.
  • the stroke amount (the value of the up and down movement) of the exhaust valve 20 is in the range of 0.5 to 1 mm. Under the above conditions, the exhaust valve 20 smoothly moves up and down in the valve chamber 12.
  • the numbers here differ depending on the equipment to be mounted and the operating conditions or the use of the fluid injection device.
  • the exhaust passage 15 is along the inner circumference of the valve chamber 12 and adjacent to the vane groove 35, opening to the valve chamber 12 and the compression chamber 31.
  • the outer peripheral shape of the valve chamber 12 and the exhaust valve 20 does not necessarily need to be circular.
  • the outer peripheral shape here is a quadrangle and a polygon, and a design in which a plurality of fluid passages are added between the inner circumference of the valve chamber 12 and the outer circumference of the exhaust valve 20 may be employed, that is, the outer peripheral wall of the exhaust valve 20 may be A plurality of fluid passages spaced apart in the circumferential direction are defined between the inner peripheral wall of the valve chamber 12.
  • the disk-shaped leaf spring 21 can be represented as 21a, 22b, 21c, it is easy to expand the design according to the gist of the present invention.
  • a coil spring can be used instead of the leaf spring 21, a coil spring can be used instead.
  • the shape of the exhaust passage 15 connected along the inner circumference of the valve chamber 12 shown in Fig. 6 is such that the fluid resistance in the direction from the exhaust hole 11 to the exhaust passage 15 is small, and the fluid resistance in the reverse direction becomes large. That is, depending on the flow direction of the exhaust passage 15, the flow line between the open end of the exhaust passage 15 and the exhaust hole 11 is different.
  • the left diagram is the discharge of the refrigerant from the exhaust hole 11 in the direction of the exhaust passage 15, and the right diagram is the reverse flow of the refrigerant from the exhaust passage 15 toward the exhaust hole 11.
  • the exhaust valve 20 is indicated by a broken line.
  • the flow line of the reverse flow refrigerant is a rectifying line along the inner circumference of the valve chamber 12, and most of them flow along the outer peripheral gap formed between the upper surface of the exhaust valve 20 and the disc-shaped leaf spring 21. Therefore, the amount of the reverse flow refrigerant to the exhaust hole 11 disposed at the center of the valve chamber 12 is greatly reduced.
  • the posture of the exhaust valve 20 (parallelism with respect to the valve seat 12a) is further stabilized along the countercurrent line on the outer circumference of the upper surface of the exhaust valve 20, and the homing time to the valve seat 12a is shortened.
  • the refrigerant resistance from the vent hole 11 to the compression chamber 31 is less and less, and on the other hand, the refrigerant flow from the compression chamber 31 to the vent hole 11 is less. Therefore, the efficient fluid injection device 10 is completed. For example, when the maximum speed (120 times per second) of a rotary compressor equipped with a variable frequency motor is used, the responsiveness of the exhaust valve 20 can be improved. Further, the reverse flow to the exhaust hole 11 becomes a re-expansion loss to the suction stroke of the next compression chamber 31, resulting in a decrease in compression efficiency.
  • Fig. 7 is a design in which the fluid injection device 10 is provided on the side of the main bearing 50, and the valve chamber 12 is bored in the cylinder plane 32a as in Fig. 3. That is, with the cylinder plane 32a as a reference surface, the fluid injection device 10 of Fig. 7 has a plane symmetrical relationship with respect to the fluid injection device of Fig. 3. However, FIG. 7 is provided with a refrigerant injection pipe 40 on the side of the main bearing 50. Also, in order to open the hole in the compression chamber 31, the exhaust passage 15 must be lengthened a little. As shown in the design example, a fluid injection device 10 that opens a hole in the cylinder plane 32b may be provided on the plane of the cylinder plane 32b or the sub-bearing 60.
  • Fig. 8 is a view showing a design in which a groove 52 is added to the side of the main bearing 50 instead of the leaf spring 21.
  • the groove 52 is at the exhaust valve 20 When the stroke amount is maximum, the exhaust valve 20 is easily detached from the plane of the main bearing 50, and the responsiveness of the exhaust valve 20 is improved. Therefore, it can be used as an alternative to the leaf spring 21. It is also possible to accommodate the coil spring in the groove 52 as a pressing means of the exhaust valve 20.
  • the second embodiment shown in Fig. 9 is a design in which the fluid injection device 10a and the fluid injection device 10b are provided in the intermediate partition 55 disposed between the cylinder 30a and the cylinder 30b provided in the compression mechanism portion of the twin-cylinder rotary compressor 90.
  • valve chambers of the two opposing fluid injection devices are each open to the cylinder faces of the cylinders 30a and 30b.
  • the refrigerant flowing into the refrigerant injection pipe 40 is equally branched into the fluid injection device 10a and the fluid injection device 10b, and flows into the compression chamber 31a and the compression chamber 31b, respectively.
  • the refrigerant injection method of the two compression chambers not only increases the amount of refrigerant injection, but also reduces the compression torque of the respective compression chambers, thereby having an effect of preventing an increase in vibration of the compressor.
  • the slit groove 75a may be added to one of the upper and lower surfaces of the slider 75 that connects the cylinder flat 32a or the cylinder flat 32b to avoid the above problem.
  • a slit groove 75a is added from the tip end of the slider 75 from the range of S1 to S2, and the tip end of the exhaust passage 15 is opened to the slit groove 75a.
  • the rotation angle ⁇ of the rolling piston 78 that is eccentrically rotated counterclockwise is an instant of 90° from the center line of the slider 75, and one end (size S1) of the slit groove 75a opens to the high pressure chamber 33a.
  • valve chamber 12 and the high pressure chamber 33a communicate via the slit groove 75a and the exhaust passage 15, the exhaust valve 20 is opened, and the refrigerant of the exhaust hole 11 is injected into the high pressure chamber 33a via the slit groove 75a. If the rotation angle ⁇ of the rolling piston is 90°, since the suction hole 7 is in the low pressure chamber 33b, the refrigerant injected in the high pressure chamber 33a does not flow out to the suction hole 7.
  • the rotation angle of the rolling piston 78 is increased, and the exhaust valve 20 closes the vent hole 11 at a moment when the pressure of the high pressure chamber 33a is higher than the refrigerant injection pressure (Pi).
  • the rotation angle ⁇ of the rolling piston 78 is, for example, 180°, the exhaust hole 11 is closed.
  • the high pressure refrigerant from the high pressure chamber 33a to the valve chamber 12 can be prevented from flowing back.
  • the value of S1 determines the refrigerant injection start angle.
  • the value of S2 is set so that the exhaust passage 15 is always opened in the slit groove 75a.
  • the value of S2 it is considered that the exhaust passage 15 is closed before the rotation angle ⁇ of the rolling piston 78 reaches 180°.
  • the refrigerant injection start angle and the injection stop angle are determined in accordance with the rotation angle ⁇ of the rolling piston 78.
  • the refrigerant injection pipe 40 of the first embodiment is used as the lubricating oil injection pipe 45, and is connected to the oil separator 83 added to the refrigeration cycle apparatus.
  • the lubricating oil captured by the oil separator 83 is discharged from the exhaust pipe 5, and is returned to the rotary compressor 1 by the pressure difference between the oil separator 83 and the compression chamber 31, and is discharged from the compression mechanism portion 4 to the return oil pool 8 together with the discharge refrigerant.
  • the rotary compressor of the present invention is mounted in an apparatus such as an air conditioner, a freezing machine, or a water heater.
  • the present invention can be applied to a housing low pressure rotary compressor and a horizontal rotary compressor.
  • the exhaust device of the present invention is simple in design and easy to manufacture.
  • the problem to be solved by the invention is to simplify the fluid injection device of the compression chamber of the rotary compressor, improve fluid injection efficiency, and improve versatility and manufacturability.
  • An annular exhaust valve that opens and closes the cylinder plane is provided with an exhaust valve that opens and closes the exhaust port. According to the rotation of the piston and the pressure fluctuation of the compression chamber, the exhaust valve is switched to perform refrigerant injection and stop injection.
  • a fluid injection device can be disposed on both sides of the intermediate partition.
  • the structure is simple, the fluid injection device has high fluid injection efficiency and reliability, and the manufacturability is superior.
  • the amount of refrigerant injection can be controlled to prevent outflow to the low pressure side.
  • it can be used in combination with a lubricating oil injection device.
  • the first feature "on” or “under” the second feature may be a direct contact of the first and second features, or the first and second features may be indirectly through an intermediate medium, unless otherwise explicitly stated and defined. contact.
  • the first feature "above”, “above” and “above” the second feature may be that the first feature is directly above or above the second feature, or merely that the first feature level is higher than the second feature.
  • the first feature “below”, “below” and “below” the second feature may be that the first feature is directly below or obliquely below the second feature, or merely that the first feature level is less than the second feature.

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Abstract

公开了一种旋转式压缩机（1）及具有其的冷冻装置。旋转式压缩机（1）包括密封的壳体（2）、压缩机构部（4）和流体注入装置（10），压缩机构部（4）包括至少一个气缸（30）、主轴承（50）、副轴承（60）、曲轴（70）、活塞（78）和滑片（75），每个气缸（30）具有对相对的两个气缸平面开口的压缩腔（31）。每个压缩腔（31）对应一个流体注入装置（10），每个流体注入装置（10）包括：对压缩腔（31）的任一气缸平面开口的阀腔（12）；对阀腔（12）开口的排气孔（11）；开关排气孔（11）的平板的排气阀（20）；对阀腔（12）和压缩腔（31）开口的排气通道（15）；与排气孔（11）连通的冷媒或者润滑油注入回路（85）；排气孔（11）与活塞（78）的偏心运行同步开关。

Description

旋转式压缩机及具有其的冷冻装置 技术领域
本发明涉及制冷领域，尤其是涉及一种旋转式压缩机及具有其的冷冻装置。
背景技术
在空调器以及冷冻装置中，防止旋转式压缩机过热的液体冷媒注入、或者提高制热能力的气体冷媒注入方式得到了普及。它们也可以作为将润滑油回收到压缩机内的润滑油回收技术进行应用。另一方面，要求对这些流体注入装置的效率进行改善，对设计和制造性进行改善。
发明内容
本发明旨在至少在一定程度上解决相关技术中的技术问题之一。
为此，本发明提出一种旋转式压缩机，流体注入装置的结构简单，提高流体注入效率、改善通用性和制造性。
本发明还提出一种具有上述旋转式压缩机的冷冻装置。
根据本发明实施例的旋转式压缩机，包括密封的壳体、压缩机构部和流体注入装置，所述压缩机构部收纳在所述壳体内，所述压缩机构部包括至少一个气缸、主轴承、副轴承、曲轴、活塞和滑片，每个所述气缸具有对相对的两个气缸平面开口的压缩腔，所述活塞在所述压缩腔中进行偏心运行，所述曲轴驱动所述活塞偏心运行，所述主轴承和所述副轴承滑动支撑所述曲轴，所述滑片与所述活塞同步进行往复运动；每个所述压缩腔对应一个所述流体注入装置，每个所述流体注入装置包括：对所述压缩腔的任一所述气缸平面开口的阀腔；对所述阀腔开口的排气孔；开关所述排气孔的平板的排气阀；对所述阀腔和所述压缩腔开口的排气通道；与所述排气孔连通的冷媒或者润滑油注入回路；所述排气孔与所述活塞的偏心运行同步开关。
根据本发明实施例的旋转式压缩机，通过采用压缩腔的压力变动实现排气孔的打开或关闭，流体注入装置的构造简单，流体注入效率和可靠性高，改善了通用性和制造性。
在本发明的一些具体实施例中，所述气缸为两个，所述两个气缸之间设有中隔板。
根据本发明的一些实施例，所述阀腔中具备将所述排气阀压紧在所述排气孔侧的板簧或者线圈弹簧。
根据本发明的一些实施例，所述气缸为一个，在所述气缸平面、和连接所述气缸平面 的所述主轴承或者所述副轴承之间、一方设有所述阀腔，另一方有与所述阀腔相对的凹槽。
在本发明的一些实施例中，在所述气缸平面、和连接所述气缸平面的所述主轴承、所述副轴承或者所述中隔板之间、一方设有所述阀腔，另一方有与所述阀腔相对的凹槽。
可选地，所述排气通道与所述排气孔偏心设置。
可选地，所述阀腔的最小内周和所述排气阀的最大外周的差为0.01到0.2mm的范围内。
在本发明的优选实施例中，所述滑片设有切口槽，通过所述滑片的往复运动，所述切口槽在所述压缩腔中改变开孔长，所述排气通道与所述阀腔和所述切口槽连通。
具体地，所述排气阀的外形为圆形或者多边形。
根据本发明实施例的冷冻装置，包括根据本发明上述实施例的旋转式压缩机。
附图说明
图1与本发明的实施例1相关，是表示旋转式压缩机内部的纵剖面图；
图2同实施例1相关，表示图1中X-X剖面图，在气缸平面配备冷媒注入装置的平面图；
图3同实施例1相关，是冷媒注入装置的纵剖面详解图；
图4同实施例1相关，是冷媒注入装置的平面详解图；
图5同实施例1相关，是冷媒注入装置的构成图；
图6同实施例1相关，表示阀腔的设计例子和冷媒的流动；
图7同实施例1相关，在主轴承配备冷媒注入装置的纵剖面图；
图8同实施例1相关，表示主轴承配备凹槽；
图9同本发明的实施例2相关，是在双气缸旋转式压缩机的中隔板中配备冷媒注入装置的纵剖面图；
图10与本发明的实施例3相关，在滑片中设有切口槽的冷媒注入装置的平面图；
图11同实施例3相关，是滑片切口槽的详解图；
图12与本发明的实施例4相关，是润滑油注入压缩腔的实际例。
附图标记：
旋转式压缩机1、壳体2、电动机3、油池8、
压缩机构部4、气缸30(30a、30b)、滚动活塞78、滑片75、曲轴70、主轴承50、副轴承60、气缸平面32a(32b)、压缩腔排气孔34、排气消音器65、滑片槽35、凹槽52、切口槽75a、吸入孔7、
流体注入装置10(10a、10b)、阀腔12、排气孔11、排气阀20、板簧21、排气通道15、冷媒通道16、阀座12a、
压缩腔31、低压腔33b、高压腔33a、
冷媒注入管40、排气管5、冷凝器80、膨胀阀81、蒸发器82、吸入管6、冷媒注入回路85、油分离器83、
双缸旋转式压缩机90、中隔板55。
具体实施方式
下面详细描述本发明的实施例，所述实施例的示例在附图中示出。下面通过参考附图描述的实施例是示例性的，旨在用于解释本发明，而不能理解为对本发明的限制。
在本发明的描述中，需要理解的是，术语“中心”、“纵向”、“横向”、“长度”、“宽度”、“厚度”、“上”、“下”、“前”、“后”、“左”、“右”、“竖直”、“水平”、“顶”、“底”“内”、“外”、“顺时针”、“逆时针”、“轴向”、“径向”、“周向”等指示的方位或位置关系为基于附图所示的方位或位置关系，仅是为了便于描述本发明和简化描述，而不是指示或暗示所指的装置或元件必须具有特定的方位、以特定的方位构造和操作，因此不能理解为对本发明的限制。
此外，术语“第一”、“第二”仅用于描述目的，而不能理解为指示或暗示相对重要性或者隐含指明所指示的技术特征的数量。由此，限定有“第一”、“第二”的特征可以明示或者隐含地包括至少一个该特征。在本发明的描述中，“多个”的含义是至少两个，例如两个，三个等，除非另有明确具体的限定。
在本发明中，除非另有明确的规定和限定，术语“安装”、“相连”、“连接”、“固定”等术语应做广义理解，例如，可以是固定连接，也可以是可拆卸连接，或成一体；可以是机械连接，也可以是电连接或彼此可通讯；可以是直接相连，也可以通过中间媒介间接相连，可以是两个元件内部的连通或两个元件的相互作用关系，除非另有明确的限定。对于本领域的普通技术人员而言，可以根据具体情况理解上述术语在本发明中的具体含义。
下面参考图1-图12对根据本发明实施例的旋转式压缩机进行详细描述，其中旋转式压缩机可以为立式压缩机、卧式压缩机、摇摆旋转式压缩机、壳体低压旋转式压缩机、双缸压缩机或者2级压缩式压缩机等。该旋转式压缩机可以应用在冷冻装置中，冷冻装置还包括冷凝器80、蒸发器82和膨胀阀81等元件。
根据本发明实施例的旋转式压缩机，包括密封的壳体2、压缩机构部4和流体注入装置10，压缩机构部4收纳在壳体2内，压缩机构部4包括至少一个气缸、主轴承50、副轴承60、曲轴70、活塞78和滑片75，每个气缸具有对相对的两个气缸平面开口的压缩腔31， 活塞78在压缩腔31中进行偏心运行，曲轴70驱动活塞78偏心运行，主轴承50和副轴承60滑动支撑曲轴70，滑片75与活塞78同步进行往复运动。
当旋转式压缩机为单缸压缩机时，主轴承50和副轴承60分别设在气缸的两个气缸平面上。当旋转式压缩机为双缸压缩机时，气缸为两个，两个气缸之间设有中隔板55，主轴承50、副轴承60和中隔板55分别设在两个气缸的气缸平面上。
每个压缩腔31对应一个流体注入装置10，每个流体注入装置10包括：对压缩腔31的任一气缸平面开口的阀腔12。对阀腔12开口的排气孔11。开关排气孔11的平板的排气阀20。对阀腔12和压缩腔开口的排气通道15。与排气孔11连通的冷媒或者润滑油注入回路85。排气孔11与活塞78的偏心运行同步开关。
由于冷媒或者润滑油注入回路85可以连接至冷凝器80和膨胀阀81之间，冷媒或者润滑油注入回路85的压力比冷凝器80的压力要低，比蒸发器82的压力高，形成冷媒注入压力(Pi)。排气阀20用于打开排气孔11，排气通道15连通压缩腔31和阀腔12，冷媒或者润滑油注入回路85与排气孔11连通，在活塞78偏心运行过程中，压缩腔31的压力发生变化，因此排气阀20的两侧会存在压力差，当冷媒或者润滑油注入回路85的压力大于阀腔12的压力时，排气阀20打开排气孔11，从冷媒或者润滑油注入回路85流进的冷媒或者润滑油通过排气孔11和排气通道15流入到压缩腔31内。
当压缩腔31内的压力大于冷媒或者润滑油注入回路85的压力时，排气阀20关闭排气孔11。由此实现根据压缩腔31的压力变化，排气阀20对排气孔11进行开闭。
可以理解的是，当气缸为一个时，流体注入装置10可以设在气缸上也可以设在主轴承50或者副轴承60上，例如在图1和图2的示例中，流体注入装置10设在气缸上。在图7的示例中，流体注入装置10设在主轴承50上。
当气缸为两个时，每个气缸对应一个流体注入装置10，每个气缸对应的流体注入装置10可以设在相应的气缸、中隔板55、该气缸对应的主轴承50或者副轴承60中的任一个上。在图9的示例中，两个流体注入装置10共用一个冷媒或者润滑油注入回路85，两个流体注入装置10设在中隔板55上。
根据本发明实施例的旋转式压缩机，通过采用压缩腔31的压力变动实现排气孔11的打开或关闭，流体注入装置10的构造简单，流体注入效率和可靠性高，改善了通用性和制造性。
在本发明的一些实施例中，阀腔12中具备将排气阀20压紧在排气孔11侧的板簧21或者线圈弹簧。从而保证排气阀20可以关闭排气孔11。
在本发明的一些实施例中，气缸为一个，在气缸平面、和连接气缸平面的主轴承50或者副轴承60之间、一方设有阀腔12，另一方有与阀腔12相对的凹槽52。也就是说，可以 在气缸上设置阀腔12和凹槽52中的其中一个，在主轴承50或副轴承60上设置阀腔12和凹槽52中的另一个，阀腔12和凹槽52相对设置，当排气阀20的行程最大时，通过设置凹槽52，凹槽52内的高压环境可以保证排气阀20可以关闭排气孔11。
在本发明的一些实施例中，气缸为两个，在气缸平面、和连接气缸平面的主轴承50、副轴承60或者中隔板55之间、一方设有阀腔12，另一方有与阀腔12相对的凹槽52。也就是说，可以在气缸上设置阀腔12和凹槽52中的其中一个，在与该气缸对应的中隔板55、主轴承50或者副轴承60上设置阀腔12和凹槽52中的另一个。从而当排气阀20的行程最大时，通过设置凹槽52，凹槽52内的高压环境可以保证排气阀20可以关闭排气孔11。
根据本发明的一些具体实施例，排气通道15与排气孔11偏心设置。
在本发明的具体示例中，阀腔12的最小内周和排气阀20的最大外周的差为0.01到0.2mm的范围内。从而保证排气阀20可以在阀腔12内顺畅地上下运动。
根据本发明的一些优选实施例，如图10和图11所示，滑片75设有切口槽75a，通过滑片75的往复运动，切口槽75a在压缩腔31中改变开孔长，排气通道15与阀腔12和切口槽75a连通。从而可以避免从冷媒或者润滑油注入回路85流进的冷媒或者润滑油进入到吸入孔7中，保证从吸入孔7吸入的冷媒量，保证旋转式压缩机的冷冻能力。
可选地，排气阀20的外形为圆形或者多边形。
根据本发明实施例的冷冻装置，包括根据本发明上述实施例的旋转式压缩机。
下面参考图1-图12对根据本发明四个具体实施例的旋转式压缩机进行详细描述。
实施例1
本发明的实施例1的形态是基于图1进行说明。
旋转式压缩机1是由在壳体2的内周固定的压缩机构部4、在其上部配置的电动机3组成。压缩机构部4是由在气缸30中具备的圆筒形的压缩腔中偏心旋转的滚动活塞78、以及与该滚动活塞78进行同期往复运动的滑片75(如图2所示)、使滚动活塞78偏心旋转的曲轴70、对曲轴70进行滑动支持的主轴承50和主轴承60等组成。在气缸平面32a的主轴承50和在气缸平面32b的副轴承60分别用5个螺钉连接。在副轴承60中设有压缩腔排气孔34和排气消音器65。
实施例1的形态是由：对气缸平面32a开口的圆形的阀腔12、对该中心开孔的排气孔11、开关排气孔11的排气阀20、将排气阀20朝排气孔11按压的板簧21、以及连通阀腔12和压缩腔31的排气通道15组成。由这些要素组成的形态称为流体注入装置10。
排气孔11对冷媒通道16开孔，在冷媒通道16中连接了对壳体2的外侧开孔的冷 媒注入管40。与壳体2的上端具备的排气管5(图12)连接的冷冻循环的冷凝器80连接了膨胀阀81和蒸发器82，蒸发器82的出口连接了固定在壳体2上的吸入管6。连接在冷凝器80和膨胀阀81之间的冷媒注入回路85连接冷媒注入管40。
在旋转式压缩机运行时，通过冷媒注入回路85的冷媒是由于其回路的阻力、或者在冷媒注入回路85途中追加连接毛细管(无图示)、还有气液分离器(无图示)等等手段而压力减小。因而，冷媒注入管40的压力比冷凝器80的压力要低，比蒸发器82的压力高，形成冷媒注入压力(Pi)。
图2是图1的X-X剖面的平面图。表示在气缸平面32a配备的流体注入装置10、连接气缸30的配管、及压缩腔31的内部。构成压缩机构部4的气缸30的中央有圆筒形的压缩腔、圆形的阀腔12对其开孔面的气缸平面32a开口、其中心设有排气孔11和阀座12a。吸入管6连接到压缩腔31的侧面。另外，收纳在阀腔12中开关排气孔11的排气阀20及板簧21(都用图3表示)无图示。
被曲轴70驱动沿反时针方向偏心旋转的滚动活塞78和与其外周滑动抵接往复运动的滑片75将压缩腔31分为：连接吸入管6的低压腔33b和连接排气通道15的高压腔33a。因而，滚动活塞78的每转时阀腔12的压力是在与吸入压力相等的低压到与吐出压力相等的高压之间变动。
图3是在图1表示的流体注入装置10的详细剖面图。图4是流体注入装置10的平面图，图5是流体注入装置10的构成零件图。
对图3的气缸平面32a中具备的流体注入装置10开口的圆形的阀腔12是在气缸平面32a上加工的圆形的槽，那个开口端连接到主轴承50的平面。在阀腔12中有阀座12a，排气孔11对其中心开孔。排气通道15对阀腔12和压缩腔31开孔。
在排气阀20上按压其外周的碟状的板簧21，通过其弹簧效果使排气阀20的上下运动平稳，并且在压缩腔31的高压冷媒逆流到阀腔12的时候使排气阀20迅速归位。
在此，作为搭载在家用空调里的旋转式压缩机的参考值，阀腔12的内径(d)约为8～12mm，阀座12a的高度为1.5～3mm。装在阀腔12里的排气阀20的板厚是0.1～0.3mm范围，其外径小于阀腔12的内径(d)，差值在0.01～0.2mm。排气阀20的行程量(上下运动的值)是在0.5～1mm的范围之内。上述条件下，排气阀20在阀腔12中顺畅地上下运动。但是，这里的数字由于搭载的机器及运行条件或者流体注入装置的用途不同等而不同。
图4里有如下特征，排气通道15是沿着阀腔12的内周，并与滑片槽35相邻，对阀腔12和压缩腔31开口。其结果有如下效果：后述阀腔12的流体元件效果，以及通过阀腔12的余隙容积降低高压冷媒的再膨胀损耗的效果。
另外，阀腔12和排气阀20的外周形状不一定需要为圆形。例如：这里的外周形状是四边形和多边形，在阀腔12的内周和排气阀20的外周之间追加多个流体通路的设计也可以采用，也就是说，排气阀20的外周壁可以与阀腔12的内周壁之间限定出在周向方向上间隔分布的多个流体通路。
还有，如图5所示，如碟状板簧21可作为21a，22b，21c表示，按本发明的主旨很容易进行扩展设计。代替板簧21的替代可以使用线圈弹簧。
沿图6所示的阀腔12的内周连接的排气通道15的形状是使得从排气孔11向排气通道15方向的流体阻力少，逆向的流体阻力变大的流体元件。即，根据排气通道15的流向，排气通道15的开口端和排气孔11之间的流线是不同。左图是从排气孔11向排气通道15的方向排出冷媒，右图是从排气通道15向排气孔11方向的冷媒逆流。另外，排气阀20用虚线表示。
在图6的左图里，排气孔11排出的冷媒在上升的排气阀20的内侧扩散流向排气通道15。这个时候排气阀20的行程量(上浮量)是最大的。
右图中，压缩腔31的高压冷媒通过排气通道15向排气孔11逆流后，通过作用在排气阀20上面的高压和板簧的压紧力，可以减少排气阀20流向排气孔11方向的行程量。
逆流冷媒的流线为沿着阀腔12的内周的整流线，其中大部分沿着排气阀20的上面和碟状形板簧21之间形成的外周间隙流动。因此，对在阀腔12中心配置的排气孔11的逆流冷媒量大幅减少。沿着排气阀20上面外周的逆流线使排气阀20的姿势(相对阀座12a的平行度)进一步稳定，缩短对阀座12a的归位时间。
其结果是，从排气孔11向压缩腔31的冷媒阻力越来越少，另一方面从压缩腔31向排气孔11的冷媒逆流变少。因此，完成了高效的流体注入装置10。例如：搭载变频电机的旋转式压缩机的最高速度(每秒120次)时，可提高排气阀20的应答性。另外，向排气孔11的逆流成为到下一个压缩腔31的吸入行程的再膨胀损失，招致压缩效率降低。
图7是在主轴承50侧配备流体注入装置10的设计，和图3一样阀腔12在气缸平面32a开孔。也就是说，以气缸平面32a作为基准面，图7的流体注入装置10是相对于图3的流体注入装置具有面对称的关系。但是，图7是在主轴承50侧配备冷媒注入管40。还有为了在压缩腔31内开孔，必须要把排气通道15加长一点。如设计例子所示，在气缸平面32b或者副轴承60的平面上，可以配备对气缸平面32b开孔的流体注入装置10。
图8是替代板簧21，在主轴承50侧追加凹槽52的设计。凹槽52在排气阀20的 行程量最大时使得排气阀20容易从主轴承50的平面脱离，具有改善排气阀20的应答性的效果。因此，可以作为板簧21的替代手段使用。也可以在凹槽52中收纳线圈弹簧作为排气阀20的压紧手段使用。
实施例2
图9展示的实施例2是在双缸旋转式压缩机90的压缩机构部中具备的气缸30a和气缸30b之间配置的中隔板55中配备流体注入装置10a和流体注入装置10b的设计。
相对的2个上述的流体注入装置的阀腔各自对气缸30a和气缸30b的气缸平面开孔。本实施例中，流入冷媒注入管40的冷媒同等分流到流体注入装置10a和流体注入装置10b中，分别各自流入压缩腔31a和压缩腔31b。
也可以在气缸30a和气缸30b中分别配备流体注入装置。而且，两个压缩腔的冷媒注入方法，不仅仅是增加冷媒注入量，各自的压缩腔的压缩力矩会变得相等，因此具有防止压缩机振动增加的效果。
实施例3
使冷媒注入压力(Pi)接近压缩腔31的排气压力(Pd)对排气孔11注入大量气体冷媒的设计中，注入的冷媒的一部分会流出到吸入孔7中。其结果，吸入冷媒量减少，冷冻能力降低。实施例3中，如图10和图11所示，连接气缸平面32a或者气缸平面32b的滑片75的上下面中任一一面可以追加切口槽75a来规避上述问题。
在图10，从滑片75的顶端开始从S1到S2的范围里追加切口槽75a，排气通道15的前端对切口槽75a开口。反时针方向偏心旋转的滚动活塞78的旋转角θ是从滑片75的中心线通过90°的瞬间，切口槽75a的一端(尺寸S1)对高压腔33a开口。
这时，经由切口槽75a和排气通道15，阀腔12和高压腔33a连通，排气阀20打开，排气孔11的冷媒经由切口槽75a注入到高压腔33a。假如滚动活塞的旋转角θ是90°，由于吸入孔7是在低压腔33b，因而在高压腔33a注入的冷媒不会流出到吸入孔7。
在那之后，滚动活塞78的旋转角增加，高压腔33a的压力高于冷媒注入压力(Pi)的瞬间排气阀20就会关闭排气孔11。这时滚动活塞78的旋转角θ例如是180°时，排气孔11就会关闭。因而，可以阻止从高压腔33a向阀腔12的高压冷媒逆流。
在上述设计中，S1的值决定冷媒注入开始角度。另一方面，S2的值是为了排气通道15常在切口槽75a里开口而设定。但是，设定S2的值时要考虑在滚动活塞78的旋转角θ在达到180°前，关闭排气通道15。在这个设计下，不管压缩腔31压力如何， 根据滚动活塞78的旋转角θ来决定冷媒注入开始角度和注入停止角度。
实施例4
图12中，使用实施例1的冷媒注入管40作为润滑油注入管45，连接在冷冻循环装置追加的油分离器83。从排气管5排出被油分离器83捕获的润滑油，由于油分离器83和压缩腔31的压力差返回旋转式压缩机1，和排出冷媒共同从压缩机构部4排出返回油池8。
本发明的旋转式压缩机搭载在空调、冷冻机器、热水器等装置中。另外，本发明可在壳体低压式旋转式压缩机和卧式旋转式压缩机中应用。本发明的排气装置设计简单，制造容易。
综上所述可知，发明要解决的课题为：对旋转式压缩机的压缩腔的流体注入装置进行简化，提高流体注入效率以及改善通用性和制造性。
解决课题的所采用的具体手段：
对气缸平面开口的圆形的阀腔中，具备了开关排气孔的排气阀。根据活塞的旋转和压缩腔的压力变动，排气阀开关，进行冷媒注入和停止注入。双缸旋转式压缩机中，可以分别在中隔板的两面配置流体注入装置。
采用上述手段为发明带来的效果：构造简单，流体注入装置的流体注入效率和可靠性高，制造性优越。根据排气孔的孔径、或者在滑片上追加切口槽，可以控制冷媒注入量，防止对低压侧的流出。另外，可以兼用于润滑油注入装置。
在本发明中，除非另有明确的规定和限定，第一特征在第二特征“上”或“下”可以是第一和第二特征直接接触，或第一和第二特征通过中间媒介间接接触。而且，第一特征在第二特征“之上”、“上方”和“上面”可是第一特征在第二特征正上方或斜上方，或仅仅表示第一特征水平高度高于第二特征。第一特征在第二特征“之下”、“下方”和“下面”可以是第一特征在第二特征正下方或斜下方，或仅仅表示第一特征水平高度小于第二特征。
在本说明书的描述中，参考术语“一个实施例”、“一些实施例”、“示例”、“具体示例”、或“一些示例”等的描述意指结合该实施例或示例描述的具体特征、结构、材料或者特点包含于本发明的至少一个实施例或示例中。在本说明书中，对上述术语的示意性表述不必须针对的是相同的实施例或示例。而且，描述的具体特征、结构、材料或者特点可以在任一个或多个实施例或示例中以合适的方式结合。此外，在不相互矛盾的情况下，本领域的技术人员可以将本说明书中描述的不同实施例或示例以及不同实施例或示例的特征进行结合和组合。
尽管上面已经示出和描述了本发明的实施例，可以理解的是，上述实施例是示例性的，不能理解为对本发明的限制，本领域的普通技术人员在本发明的范围内可以对上述实施例进行变化、修改、替换和变型。

Claims (10)

  1. 一种旋转式压缩机，其特征在于，包括密封的壳体、压缩机构部和流体注入装置，所述压缩机构部收纳在所述壳体内，所述压缩机构部包括至少一个气缸、主轴承、副轴承、曲轴、活塞和滑片，每个所述气缸具有对相对的两个气缸平面开口的压缩腔，所述活塞在所述压缩腔中进行偏心运行，所述曲轴驱动所述活塞偏心运行，所述主轴承和所述副轴承滑动支撑所述曲轴，所述滑片与所述活塞同步进行往复运动；
    每个所述压缩腔对应一个所述流体注入装置，每个所述流体注入装置包括：
    对所述压缩腔的任一所述气缸平面开口的阀腔；
    对所述阀腔开口的排气孔；
    开关所述排气孔的平板的排气阀；
    对所述阀腔和所述压缩腔开口的排气通道；
    与所述排气孔连通的冷媒或者润滑油注入回路；
    所述排气孔与所述活塞的偏心运行同步开关。
  2. 根据权利要求1所述的旋转式压缩机，其特征在于，所述气缸为两个，所述两个气缸之间设有中隔板。
  3. 根据权利要求1或2所述的旋转式压缩机，其特征在于，所述阀腔中具备将所述排气阀压紧在所述排气孔侧的板簧或者线圈弹簧。
  4. 根据权利要求1所述的旋转式压缩机，其特征在于，所述气缸为一个，在所述气缸平面、和连接所述气缸平面的所述主轴承或者所述副轴承之间、一方设有所述阀腔，另一方有与所述阀腔相对的凹槽。
  5. 根据权利要求2所述的旋转式压缩机，其特征在于，在所述气缸平面、和连接所述气缸平面的所述主轴承、所述副轴承或者所述中隔板之间、一方设有所述阀腔，另一方有与所述阀腔相对的凹槽。
  6. 根据权利要求1或2所述的旋转式压缩机，其特征在于，所述排气通道与所述排气孔偏心设置。
  7. 根据权利要求1或2所述的旋转式压缩机，其特征在于，所述阀腔的最小内周和所述排气阀的最大外周的差为0.01到0.2mm的范围内。
  8. 根据权利要求1或2所述的旋转式压缩机，其特征在于，所述滑片设有切口槽，通过所述滑片的往复运动，所述切口槽在所述压缩腔中改变开孔长，所述排气通道与所述阀腔和所述切口槽连通。
  9. 根据权利要求1或2所述的旋转式压缩机，其特征在于，所述排气阀的外形为圆形或者多边形。
  10. 一种冷冻装置，其特征在于，包括根据权利要求1-9中任一项所述的旋转式压缩机。
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