WO2015010260A1

WO2015010260A1 - Rotary compressor and refrigerating circulating apparatus having same

Info

Publication number: WO2015010260A1
Application number: PCT/CN2013/079932
Authority: WO
Inventors: 小津政雄; 梁自强; 王玲
Original assignee: 广东美芝制冷设备有限公司
Priority date: 2013-07-23
Filing date: 2013-07-23
Publication date: 2015-01-29

Abstract

A rotary compressor and a refrigerating circulating apparatus having same. The rotary compressor comprises: a seal housing (2), a lower part of the housing (2) being provided with an oil storage chamber (F); a motor (M), the motor (M) being disposed in the housing (2), and the motor (M) comprising a stator (11) having a motor winding (15) and a rotor (20), a gap being formed between an outer periphery wall of the stator (11) and an inner wall of the housing (2), and an oil separation chamber (T) being provided in the housing (2) above the motor (M); a compression apparatus (P), the compression apparatus (P) being disposed at the lower side of the motor (M) and limiting a compression chamber (52); and a winding cover (30), the winding cover (30) being disposed between the stator (11) and the compression apparatus (P), and the winding cover (30) enclosing a lower end of the motor winding (15). Oil-containing high-pressure refrigerant discharged from the compression chamber (52) flows through the winding cover (30) and the motor (M) to the oil separation chamber (T). An outer side of the winding cover (30) has an oil passage (S) connecting the oil storage chamber (F) and the oil separation chamber (T).

Description

Rotary compressor and refrigeration cycle device therewith

The present invention relates to a rotary compressor for a rotary compressor, a scroll compressor, a vane compressor, and the like which are applied to an air conditioner, a freezing machine, a water heater, etc., and a high pressure side, and includes The refrigeration cycle device of the rotary compressor. Background technique

In the rotary compressor which is a rotary compressor, the internal pressure of the seal case is used as the high pressure side for the purpose of improving the compression efficiency, the lubrication of the sliding parts, and the miniaturization of the casing volume by direct suction of the refrigerant. The crankshaft rotation axis is set to the vertical direction, and the so-called vertical type is often used. However, the vertical rotary compressor has the following problems:

1. The motor winding is overheated, resulting in motor burnout and reduced motor efficiency

If the heat exchange between the refrigerant discharged from the compression unit and the motor winding is insufficient, the motor winding will be burnt due to overheating of the motor winding, and the motor efficiency will be reduced due to the overheating. On the other hand, since the temperature of the refrigerant discharged is lowered, the comfort of the heating operation mode of the air conditioner is deteriorated.

2. Due to the increase in oil discharge and the decrease in oil superheat, it will cause compressor failure, etc.

In the compressor during defrosting operation, the amount of oil discharged is significantly increased due to the inhalation of a large amount of liquid refrigerant, and the oil level is also lowered. In addition, when the compressor is stopped, the amount of oil discharged during startup will increase significantly due to the "deposition of refrigerant" in the casing. In addition, if "oil overheating phenomenon" occurs during operation, the viscosity of the oil will be significantly reduced due to the dilution of the refrigerant after condensation in the oil. This phenomenon is the main cause of wear failure of the compressor. In addition, the performance of the heat exchanger is lowered due to the amount of oil discharged beyond the limit.

Among the above problems, the internal pressure of the casing is an essential subject in the rotary compressor of the high pressure side. As a countermeasure against this, a technique such as temperature control and rotational speed control of a refrigeration cycle apparatus including a compressor is being introduced, but the countermeasure effect is not insufficient enough, and the efficiency of the apparatus is also sacrificed. Therefore, it is necessary to study the fundamental solution of the compressor body. Summary of the invention

The present invention aims to solve at least one of the technical problems existing in the prior art. Accordingly, an object of the present invention is to provide a rotary compressor having a low fuel discharge amount and high reliability.

Another object of the present invention is to provide a refrigeration cycle apparatus having the rotary compressor.

A rotary compressor according to an embodiment of the first aspect of the present invention, comprising: a sealed casing provided with an exhaust pipe, a lower portion of the casing has an oil storage chamber in which lubricating oil is stored; a motor, the motor is provided In the housing, the The motor includes a stator having a motor winding and a rotor sleeved inside the stator, a gap between the outer peripheral wall of the stator and an inner wall of the housing, and an oil separation chamber above the motor in the housing; a compression device, the compression device being disposed on a lower side of the motor and including a crankshaft, a main bearing, a sub-bearing, and a cylinder between the main bearing and the sub-bearing, the main bearing, the sub-bearing, and the cylinder Defining a compression chamber; a winding cover, the winding cover is disposed between the stator and the compression device, and the winding cover surrounds a lower end of the motor winding, wherein the oil discharged from the compression chamber The high pressure refrigerant flows from the winding cover through the motor to the oil separation chamber; wherein an outer side of the winding cover has an oil passage that communicates between the oil reservoir and the oil separation chamber.

A rotary compressor according to an embodiment of the present invention has the following advantageous effects:

(1) The motor windings are directly cooled by the exhaust refrigerant, so motor reliability and motor efficiency can be improved. (2) Since the oil of the oil reservoir F and the refrigerant discharged from the compression member P are separated by the winding cover, even if a large amount of refrigerant flows, the oil temperature and the amount of oil in the oil reservoir F are not affected. Further, by the above-described isolation effect, the oil in the oil reservoir F can maintain an appropriate temperature, and condensation of the refrigerant in the oil does not occur.

(3) Since there is no pressure difference between the oil separation chamber T and the oil reservoir chamber F, the oil separated in the oil separation chamber T can easily flow from the oil passage S to the oil reservoir chamber F. Therefore, the amount of oil discharged from the exhaust pipe is small, and the oil reservoir F can usually maintain an appropriate amount of oil.

In addition, since the oil reservoir F includes a gap between the outer circumference of the winding cover and the casing, the capacity of the oil reservoir F is sufficient.

Further, the rotary compressor according to the present invention has the following additional technical features:

According to an embodiment of the invention, the exhaust pipe is connected to the housing at the oil separation chamber or the oil passage.

According to an embodiment of the invention, the oil passage is defined by an outer side of the winding cover, a gap between the stator and the housing.

According to another embodiment of the present invention, the oil passage is constituted by a pipe provided outside the casing, and both ends of the pipe are connected to the oil reservoir and the oil separation chamber, respectively.

According to an embodiment of the present invention, the winding cover includes: a first column segment, an upper end of the first column segment is sleeved outside the stator; a second column segment, the second column segment is disposed at Below the first column segment, and the inner diameter of the second column segment is smaller than the inner diameter of the first column segment, and the second column segment is sleeved outside the upper end of the main bearing of the compression device And a connecting section, the connecting section has an inverted truncated cone and is connected between the first column section and the second column section.

According to an embodiment of the present invention, a plurality of core cuts are formed on an outer peripheral wall of the stator, and each of the core cuts is formed by cutting a part of an outer circumference of the stator, and the plurality of core cuts are penetrated In the axial direction of the stator, the outer peripheral wall of the stator forms the gap between the core cutout and the inner wall of the housing. According to an embodiment of the present invention, a plurality of the core cutouts of the stator are respectively recessed inwardly to form a core slot, the core slot extending through an axial direction of the stator; a plurality of protrusions extending upward from an outer side of the upper end of the first column segment, the number of the protrusions being less than the number of the core slots, each of the protrusions being embedded in a lower end of the corresponding core slot to cover the winding The upper end is mated with the stator.

Optionally, the lower end of the second column segment of the winding cover extends outwardly from the flange; the rotary compressor further includes a spring, and the two ends of the spring respectively abut against the lower surface of the flange and The upper surface of the cylinder is such that the upper end surface of the first column segment abuts against the lower surface of the stator. According to an embodiment of the invention,

Preferably, the core cut includes four and is evenly distributed in the circumferential direction, and the protrusions are opposite ones.

According to an embodiment of the present invention, the rotary compressor further includes: an auxiliary winding cover, the auxiliary winding cover is disposed above the motor and surrounds an upper end of the motor winding, and a peripheral wall of the auxiliary winding cover There are a plurality of outer peripheral holes, and a vent hole is formed in the center.

According to an embodiment of the present invention, the auxiliary winding cover is formed as an inverted buckle-shaped structure, and the lower end of the auxiliary winding cover extends downwardly from the two auxiliary protrusions, and the two auxiliary protrusions are embedded in the corresponding iron The upper end of the core groove is adapted to engage the lower end of the auxiliary winding cover with the stator.

Optionally, the housing includes: an upper casing, the upper casing is connected to the exhaust pipe, and a lower surface of the upper casing is provided with a coil spring disposed in an up and down direction; a lower casing, a The lower case is connected below the upper case, wherein the motor, the compression device, the winding cover and the auxiliary winding cover are both disposed in the lower case, wherein the coil spring The lower end is abutted on the upper surface of the auxiliary winding cover and has a position corresponding to the exhaust hole.

According to an embodiment of the invention, the upper end of the crankshaft is provided with a circular plate disposed coaxially therewith.

According to an embodiment of the invention, the upper side wall of the winding cover is provided with a bypass hole therethrough.

Optionally, the winding cover is further provided with a differential pressure valve, and the differential pressure valve is disposed corresponding to the bypass hole to open or close the bypass hole according to a pressure difference between the inner side and the outer side of the winding cover.

Preferably, the differential pressure valve is a reed valve and includes a main valve and an auxiliary valve fixed to an outer sidewall of the winding cover. According to an embodiment of the invention, the motor uses a variable frequency motor in which the motor winding is a concentrated winding method. According to an embodiment of the present invention, the rotary compressor further includes: an exhaust muffler between the motor and the main bearing, the exhaust muffler having a muffler exhaust port, the muffling The exhaust port is sleeved on the hub of the main bearing; the compression device has a double cylinder therein, and the outer diameter of the flange of the main bearing is fixed on the inner wall of the casing.

Optionally, the winding cover is formed into a bowl-like structure and a circular hole is formed in the center, the circular hole is fitted with an outer diameter of the muffler exhaust port; the motor M has a winding disposed at the winding An outer winding insulation frame, wherein an inner diameter of the winding cover is fitted to the winding insulation frame such that a lower end of the motor winding is covered by the winding cover.

Further optionally, the rotary compressor further includes a second spring, the second spring is abutted on the winding cover Between the lower surface and the upper surface of the exhaust muffler.

According to an embodiment of the invention, the winding cover is made of a non-conductive material or a non-conductive material.

A refrigeration cycle apparatus according to an embodiment of the second aspect of the present invention, comprising: a rotary compressor according to an embodiment of the first aspect of the present invention; a condenser connected to an exhaust pipe in the rotary compressor; An evaporator, the evaporator being connected to the condenser through an expansion device; and a reservoir connected between the evaporator and an intake pipe communicating with the compression chamber.

The refrigeration cycle apparatus further includes: a refrigerant injection pipe, one end of the refrigerant injection pipe is connected to a connection passage of the condenser and the expansion device, and the other end is connected to a flange side of the sub-bearing and is pressed The contraction chamber is connected.

A flow regulating valve is disposed on the refrigerant injection pipe.

The refrigeration cycle apparatus further includes: a temperature sensor, the temperature sensor is connected to the exhaust pipe; and a control device, the control device is connected to the temperature sensor.

The additional aspects and advantages of the invention will be set forth in part in the description which follows. DRAWINGS

The above and/or additional aspects and advantages of the present invention will become apparent and readily understood from

BRIEF DESCRIPTION OF THE DRAWINGS Fig. 1 is a longitudinal sectional view and a refrigerating cycle apparatus view of an internal constitution of a rotary compressor according to a first embodiment of the present invention;

Figure 2 is a schematic view of the winding cover of the rotary compressor shown in Figure 1;

Figure 3 is a cross-sectional view showing the arrangement relationship of the motor, the winding cover, and the like of the rotary compressor shown in Figure 1. Figure 4 is a view showing the operating body, the oil separation chamber, and the oil passage in the rotary compressor shown in Figure 1. An internal structure diagram between S and the oil reservoir;

Figure 5 is a comparison view of the temperature of each portion of the rotary compressor shown in Figure 1 when comparing the presence or absence of the winding cover; Figure 6 is a detailed sectional view of the compression device of the rotary compressor shown in Figure 1;

Figure 7 is a schematic view of one example of the rotary compressor shown in Figure 1, in which the exhaust pipe configuration is changed; Figure 8 is a schematic view of another example of the rotary compressor shown in Figure 1, in which the oil passage design Fig. 9 is a schematic view showing still another example of the rotary compressor shown in Fig. 1, in which the oil passage design is changed; Fig. 10 is a schematic view of the rotary compressor according to the second embodiment of the present invention, in which the frequency conversion is applied Two-cylinder rotary compressor, and the design of the winding cover changes;

Figure 11 is a schematic view showing a further variation of the rotary compressor shown in Figure 10; Figure 12 is a schematic view of a rotary compressor in accordance with a third embodiment of the present invention;

Figure 13 is a schematic view of a rotary compressor in accordance with a fourth embodiment of the present invention;

Figure 14 is a schematic view of a refrigeration cycle apparatus according to a fifth embodiment of the present invention;

Figure 15 is a schematic illustration of a refrigeration cycle apparatus in accordance with a second embodiment of the present invention. detailed description

The embodiments of the present invention are described in detail below, and the examples of the embodiments are illustrated in the drawings, wherein the same or similar reference numerals are used to refer to the same or similar elements or elements having the same or similar functions. The embodiments described below with reference to the drawings are intended to be illustrative only and not to limit the invention.

In the description of the present invention, it is to be understood that the terms "central", "upper", "lower", "left",

The orientation or positional relationship of "right", "vertical", "horizontal", "top", "bottom", "inside", "outside", etc. is based on the orientation or positional relationship shown in the drawing, only for The invention is not limited by the scope of the invention, and is not intended to be a limitation of the invention. Moreover, the terms "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. Thus, features defining "first" and "second" may include one or more of the features, either explicitly or implicitly. In the description of the present invention, "multiple" means two or more unless otherwise stated.

In the description of the present invention, it should be noted that the terms "installation", "connected", and "connected" should be understood broadly, and may be fixed or detachable, for example, unless otherwise explicitly defined and defined. Connected, or connected in one piece; can be directly connected, or indirectly connected through an intermediate medium, and can be internal to the two elements. The specific meaning of the above terms in the present invention can be understood in a specific case by those skilled in the art.

In the present invention, the first feature "on" or "below" the second feature may include direct contact of the first and second features, and may also include first and second features, unless otherwise explicitly defined and defined. It is not in direct contact but through additional features between them. Moreover, the first feature "above", "above" and "above" the second feature includes the first feature directly above and above the second feature, or merely indicating that the first feature level is higher than the second feature. The first feature "below", "below" and "below" the second feature includes the first feature being directly above and above the second feature, or merely indicating that the first feature level is less than the second feature.

A rotary compressor RC according to an embodiment of the first aspect of the present invention, which can be used for a rotary compressor of an air conditioner, a freezing machine, a water heater, etc., vortex, is described below with reference to Figs. Compressors and vane compressors, etc.

A rotary compressor according to an embodiment of the present invention includes: a sealed casing 2, a motor M, and a compression device P And winding cover 30.

As shown in Fig. 1, an exhaust pipe 3 is disposed on the sealed casing 2, and a lower portion of the casing 2 has an oil reservoir F in which lubricating oil is stored. The motor M is disposed in the casing 2, and the motor M includes a stator 11 having a motor winding 15 and a rotor 20 sleeved inside the stator 11. The outer peripheral wall of the stator 11 has a gap with the inner wall of the casing 2, and the casing 2 is located therein. There is an oil separation chamber T above the motor M. The compression device is disposed on the lower side of the motor cymbal and includes a crankshaft 60, a main bearing 53, a sub-bearing 57, and a cylinder 51 between the main bearing 53 and the sub-bearing 57, between the main bearing 53, the sub-bearing 57 and the cylinder 51 A compression chamber 52 is defined. The winding cover 30 is disposed between the stator 11 and the compression device 且 and the winding cover 30 surrounds the lower end of the motor winding, wherein the oil-containing high-pressure refrigerant discharged from the compression chamber 52 is turbulent from the winding cover 30 through the motor to the oil separation chamber. . The outer side of the winding cover 30 has an oil passage S that communicates with the oil reservoir F and the oil separation chamber. The winding cover 30 is made of a non-conductive material or a non-conductive material.

Thus, in the rotary compressor shown in Fig. 1, the winding cover 30 is provided between the main bearing 53 and the stator 11, the exhaust hole 54 provided with the main bearing 53, and the winding end portion of the stator 11 are the winding cover 30. Encircled. Therefore, the oil-containing high-pressure refrigerant discharged from the main bearing 53 flows from the winding cover 30 through the motor winding 15 to the oil separation chamber T.

During this period, the high pressure refrigerant exchanges heat directly with the motor windings 15, cooling the entire motor winding 15, and also heating the high pressure refrigerant on the other side. By this heating, the oil and the refrigerant are separated, and the refrigerant flows from the exhaust pipe 3 to the refrigeration cycle device. The oil on the other side, through several oil passages s, can be returned to the oil reservoir F at the same pressure as the oil separation chamber T without resistance.

(1) The motor winding 15 is directly cooled by the discharged refrigerant, so that the reliability of the motor and the efficiency of the motor can be improved. (2) Since the oil of the oil reservoir F and the refrigerant discharged from the compression member P are separated by the winding cover 30, even if a large amount of refrigerant flows, the oil temperature and the amount of oil in the oil reservoir F are not affected. Further, by the above-described isolation effect, the oil in the oil reservoir F can maintain an appropriate temperature, and condensation of the refrigerant in the oil does not occur.

(3) Since there is no pressure difference between the oil separation chamber T and the oil reservoir chamber F, the oil separated in the oil separation chamber T can easily flow from the oil passage S to the oil reservoir chamber F. Therefore, the amount of oil discharged from the exhaust pipe 3 is small, and the oil storage chamber F can usually maintain an appropriate amount of oil.

Further, since the oil reservoir chamber F includes a gap between the outer circumference of the winding cover 30 and the casing 2, the capacity of the oil reservoir chamber F is sufficient.

According to some embodiments of the invention, the exhaust pipe 3 is connected to the casing 2 at the oil separation chamber T (as shown in Fig. 1) or to the casing 2 at the oil passage S, as shown in Fig. 7. .

In an embodiment of the invention, the oil passage S is defined by the outer side of the winding cover 30 and the gap between the stator 11 and the housing 2, as shown in Fig. 1, Fig. 4, Fig. 7-8, Fig. 10-Fig. 15 is shown.

In another embodiment of the invention, the oil passage S is formed by a pipe provided outside the casing 2, two of the pipes The ends are connected to the oil reservoir F and the oil separation chamber T, respectively, as shown in FIG.

As shown in FIG. 2, the winding cover 30 includes: a first column section 301, a second column section 302, and a connecting section 303. The upper end of the first column section 301 is sleeved outside the stator 11, the second column section 302 is disposed below the first column section 301, and the inner diameter of the second column section 302 is smaller than the inner diameter of the first column section 301, the second column The segment 302 is sleeved outside the upper end of the main bearing 53 of the compression device. The connecting section 303 has an inverted truncated cone and is connected between the first column section 301 and the second column section 302.

In a specific embodiment of the present invention, as shown in FIGS. 1-3, a plurality of core cutouts 13 are formed on the outer peripheral wall of the stator 11, and each of the core cutouts 13 is formed by cutting a part of the outer circumference of the stator 11. Formed, a plurality of core cuts 13 penetrate the axial direction of the stator 11, and a peripheral wall of the stator 11 forms a gap between the outer wall of the stator 11 and the inner wall of the casing 2 through the core cut 13 . Preferably, the plurality of core cutouts 13 of the stator 11 are respectively recessed inwardly to form a core groove 13a, the core groove 13a penetrates the axial direction of the stator 11 and the upper end of the first column section 301 of the winding cover 30 is outside. A plurality of protrusions 35 are extended upward, the number of protrusions being less than the number of core slots 13a, each of which is embedded in the lower end of the corresponding core groove 13a to engage the upper end of the winding cover 30 with the stator 11. Further preferably, the core slit 13 includes four and is evenly distributed in the circumferential direction, and the projections are two opposite.

As shown in Figure 2, the lower end of the second column section 302 of the winding cover 30 extends outwardly out of the flange 304. Preferably, the rotary compressor further includes a spring 40, the two ends of the spring 40 respectively abut against the lower surface of the flange 304 and the upper surface of the cylinder to stop the upper end surface of the first column section 301 against the stator 11 On the surface.

In still other embodiments of the present invention, the rotary compressor RC further includes: an auxiliary winding cover 44, as shown in FIG. 13, the auxiliary winding cover 30 is disposed above the motor M and surrounds the upper end of the motor winding, the auxiliary winding The peripheral wall of the cover 30 has a plurality of outer peripheral holes 44a, and a vent hole 44b is formed in the center. Specifically, the auxiliary winding cover 44 is formed as an inverted bowl-shaped structure, and the lower end of the auxiliary winding cover 44 extends downwardly from the two auxiliary protrusions 35b, and the two auxiliary protrusions 35b are embedded in the upper end of the corresponding core groove 13a to assist The lower end of the winding cover 44 is engaged with the stator 11.

As shown in FIG. 13, optionally, the casing 2 includes an upper casing 2a and a lower casing 2b. The upper casing 2 is connected to the exhaust pipe 3, and the lower casing of the upper casing 2 is provided with coils arranged in the up and down direction. Spring 45. The lower casing 2 is connected below the upper casing 2, wherein the motor ^ compression device? The winding cover 30 and the auxiliary winding cover 44 are both disposed in the lower casing 2, wherein the lower end of the coil spring abuts on the upper surface of the auxiliary winding cover 44 at a position corresponding to the vent hole 44b.

As shown in Fig. 1, in some preferred embodiments of the present invention, the upper end of the crankshaft 60 is provided with a circular plate 70 disposed coaxially therewith. Thereby, the circular plate 70 fixed to the upper end of the crankshaft 60 rotates and mixes the refrigerant, so that heavy oil is splashed on the inner wall side of the casing 2 due to the centrifugal force, and therefore, the circular plate 70 has the function of promoting oil separation and returning to the oil reservoir. The role of F.

According to still another embodiment of the present invention, as shown in Fig. 12, the upper side wall of the winding cover 30 is provided with a bypass hole 33 therethrough. Thereby, a part of the discharge refrigerant escapes to the outside of the winding cover 30, and the amount of refrigerant from the winding cover 30 to the inside of the motor M can be reduced. Optionally, as shown in FIG. 12, the winding cover 30 is further provided with a differential pressure valve 37, and the differential pressure valve is disposed corresponding to the bypass hole 33 to open or close the bypass hole 33 according to the pressure difference between the inner side and the outer side of the winding cover 30. . Preferably, the differential pressure valve 37 is a reed valve and includes a main valve 37a and an auxiliary valve 37b fixed to the outer side wall of the winding cover 30.

As shown in FIG. 10, according to still other embodiments of the present invention, the motor M adopts a motor winding 15 as a centralized winding type inverter motor. The rotary compressor RC further includes: an exhaust gas between the motor M and the main bearing 53. The muffler 55, the exhaust muffler 55 has a muffler exhaust port 56, and the muffler exhaust port 56 is sleeved on the hub of the main bearing 53. The compression device P has a double cylinder therein, and the outer diameter of the flange of the main bearing 53 is fixed on the inner wall of the casing 2, wherein the winding cover 30 is formed into a bowl-like structure and a circular hole is formed in the center, and a circular hole It is fitted to the outer diameter of the muffler exhaust port 56. The motor M has a winding insulating frame 17 disposed outside the winding, wherein the inner diameter of the winding cover 30 is fitted to the winding insulating frame 17 so that the lower end of the motor winding is covered by the winding cover 30.

Optionally, the rotary compressor further includes a second spring 41 that abuts between the lower surface of the winding cover 30 and the upper surface of the exhaust muffler 55 such that the winding cover 30 faces the stator core 12 The direction is pressed to prevent vibration of the winding cover 30. However, in a state where the winding cover 30 is fixed to the winding insulating frame 17, the second spring 41 can be omitted.

A rotary compressor RC according to various embodiments of the present invention will now be described with reference to Figs.

Embodiment 1,

Fig. 1 is a view showing the basic configuration of a rotary compressor RC of the first embodiment and an outline of a refrigeration cycle device connected thereto. The vertical rotary compressor RC is composed of a compression member P attached to the inner circumference of the sealed cylindrical casing 2, and a motor M disposed on the upper side thereof, and an oil reservoir F provided in the casing 2 The oil is sealed in the middle 6.

The motor M is a stator 11 fixed to the housing 2 and a motor rotor fixed to the crankshaft 60 of the compression member P

20 composition. The stator 11 is composed of a stator core 12 made of an electromagnetic steel sheet and a motor winding 15 wound around the inner diameter side thereof. The winding end face 15a and the winding end face 15b are disposed at the upper end and the lower end of the motor winding 15, respectively.

Between the upper end of the compression member P and the lower end of the stator 11, a vent hole 54 surrounding the main bearing 53 of the compression member P and all the winding covers 30 of the winding end portion 15a are provided. As shown in Fig. 2, the winding cover 30 is composed of a combination of a cylindrical shape and a conical shape in which the upper opening portion 31b and the lower opening portion 31a are disposed, and two projections 35 are provided on the upper opening portion 31b.

The inner circumference of the lower opening portion 31a of the winding cover 30 is the outer circumference of the flange of the main bearing 53 in which the compression member P is fitted, and there is a gap between the inner circumference of the upper opening portion 31b and the outer circumference of the winding end surface 15a. Further, the inner diameter of the coil-shaped spring 40 is slightly larger than the outer circumference of the flange of the main bearing 53, and the upper opening portion 31b of the winding cover 30 is pressed against the lower surface of the stator core 12 due to the elastic force. Therefore, the winding cover 30 can be reliably mounted between the upper portion of the compression member P and the lower end of the stator core 12. Further, as will be described later, since the two projections 35 are fitted to the core grooves 13a on the outer circumference of the stator core 12, the winding cover 30 can be fixed at the correct position. In addition, the winding cover 30 The design shape of the spring 40 and the shape of the spring 40 can be appropriately changed in accordance with the gist of the present invention.

Therefore, the action body D indicated by "D" in Fig. 1 can be completed by the communication between the compression member P and the winding cover 30 and the motor M. The operating body D is composed of a compression member P, a winding cover 30, and a motor M, and also includes a circular plate 70 fixed to the upper ends of the motor rotor 20 and the crankshaft 60. The operation body D described is an oil-containing high-pressure refrigerant that is discharged from the compression member P that performs the compression activity and that is discharged from the compression member P, flows from the winding cover 30 through the inside of the motor M, and flows from the upper opening portion of the motor M to the upper portion of the motor M. An assembly of oil separation chambers T.

Fig. 3 is an X-X cross section of Fig. 1, showing the details of the lower side portion of the motor M, the arrangement of the winding cover 30, and the relationship between the four core cutouts 13 provided on the outer circumference of the stator core 12 and the casing 2. The core cutout 13 has a core groove 13a at the center, and a projection 35 of the winding cover 30 is fitted to the opposite core slots 13a. Therefore, the upper opening portion 31b of the winding cover 30, which is tightly connected to the lower side plane of the stator 1, and the outer circumference of the holding winding cover 15a are fixed to the stator 11 with a certain gap therebetween. Therefore, efforts are made to prevent it from becoming loose due to vibration through the compressor and refrigerant flow inside the winding cover 30.

The four gaps formed between the four core cuts 13 and the inner circumference of the casing 2 are referred to as oil passages S. In the present invention, the four oil passages S are passages through which the oil flows from the separation chamber T. The stator is directly fixed to the rotary compressor inside the casing. Usually, there are 2 to 6 iron core cuts of the same shape, which serve as passages for the refrigerant and the oil. In addition, the motor efficiency is reduced in proportion to the size of the cross section of the core cut. However, as will be described later, since the oil passage S of the present invention does not become a refrigerant passage, it is advantageous in that the cross-sectional area can be reduced to improve the efficiency of the motor.

Fig. 4 shows the operating body D and the space cavity formed inside the casing 2. The space cavity can be divided into three chambers as follows. That is, the junction from the bottom surface of the casing 2 to the winding cover 30 and the stator core 12 is a range of the oil reservoir chamber F in which oil can be stored. Further, from the upper surface of the stator core 12 to the ceiling surface of the casing 2, the oil separation chamber T separates the mixed refrigerant flowing out of the operating body D, and is a chamber for separating the refrigerant and the oil. Next, the four core cuts 13 connecting the oil separation chamber Τ and the stator core 12 of the oil reservoir F are the oil passages S, and the oil separated from the refrigerant in the oil separation chamber T is dropped to the oil reservoir F. aisle. Further, the exhaust pipe 3 is disposed in the oil separation chamber T in the first embodiment.

Since the oil flowing out of the oil separation chamber T can be secured in the oil reservoir F, the oil level of the oil reservoir F rises. Therefore, if the oil storage amount of the oil reservoir F is increased, the oil can also be stored in a part of the oil passage S. In the operation, the maximum oil level of the conventional rotary compressor is near the joint between the cylinder and the main bearing. Therefore, in the first embodiment, the oil storage chamber F has a larger oil retention amount than in the prior art. 10 to 20%, in addition, the oil surface can be increased to more than 20%. Further, due to the effect of increasing the capacity of the oil reservoir F, when the capacity of the refrigeration cycle apparatus is increased, the amount of oil enclosed in the compressor can be easily added.

Here, since the mixed refrigerant discharged from the compression member P does not pass through the oil reservoir F and the oil passage S, it does not matter the size of the oil passage S. Generally, the pressure of the oil separation chamber T is the same as the pressure of the oil reservoir F. . Therefore, the oil channel S If there is an area of oil drop, it is possible to reduce the number of core cuts 13 or the cross-sectional area compared with the prior art, and it is possible to improve the efficiency of the motor M.

Next, the flow state of the refrigerant and the oil in the refrigeration cycle apparatus will be briefly described with reference to Fig. 1 . The low-pressure refrigerant and the circulating oil sucked into the compression chamber 52 of the compression member P from the suction pipe 9 are passed through the sliding portion due to the pressure difference between the oil reservoir F (high pressure) and the compression chamber 52 (low pressure to high pressure) The oil that has flowed into the compression chamber 52 with the gap is mixed, and becomes a mixed refrigerant having a large oil ratio. Here, if the ratio of the circulating oil amount of the refrigeration cycle apparatus to the circulating refrigerant is OCR (oil circulation ratio), the OCR is usually 1% or less in the steady state of the apparatus. On the other hand, the oil supply amount of the oil reservoir F to the compression chamber 52 is several times or more of the above OCR.

The above-mentioned mixed refrigerant is compressed in the compression chamber 52 and discharged from the exhaust hole 54 into the winding cover 30, and mixed with the oil which completes the lubrication of the main bearing 53. The mixed refrigerant, which adds more oil in the winding cover 30, the gap through the motor winding 15, and a portion flows through the air gap 25 into the oil separation chamber T.

In the rotary compressor RC which presses the inside of the casing to the high pressure side, since the compression chamber 52 directly inhales the low-temperature low-pressure refrigerant, the temperature of the mixed refrigerant discharged by the adiabatic compression of the compression chamber 52 is the gas of the casing 2. The lowest temperature in the atmosphere, on the other hand, the temperature of the motor winding 15 is the highest. Therefore, the mixed refrigerant discharged into the winding cover 30 can be efficiently exchanged with the motor winding 15 before being passed from the winding 30 to the oil separation chamber T. That is, the motor winding 15 is cooled and the mixed refrigerant is heated.

The heated mixed refrigerant, although the quality of the refrigerant is lowered, but the dispersed oil increases the mass and flows to the oil separation chamber T, and the mixed refrigerant can be easily separated into a refrigerant and an oil. The refrigerant after separation of the oil is discharged from the exhaust pipe 3 to the condenser C, and is returned from the intake pipe 9 to the compression chamber 52 through the expansion valve V, the evaporator E, and the accumulator A.

On the other hand, the oil separated from the refrigerant falls from the oil passage S into the oil reservoir F, and the oil reservoir

The amount of oil that F has consumed can be recovered. Therefore, the refrigerant circulation device including the compressor repeats the circulation of the refrigerant and the oil. Further, the circular plate 70 fixed to the upper end of the crankshaft 60 rotates and mixes the refrigerant, so that heavy oil may splash on the inner wall side of the casing 2 due to the centrifugal force, and therefore, the circular plate 70 has the function of promoting oil separation and returning to the oil reservoir F. The role.

As described above, in the present invention, since the oil of the oil separation chamber T can fall into the oil reservoir F without resistance, the amount of oil discharged from the exhaust pipe 3 can be greatly reduced. In addition, it is ensured that the oil in the oil reservoir F, because the rotating refrigerant in the rotating rotor 20 and the compression chamber 52 is not stirred, can ensure high oil storage and oil level. Therefore, not only the margin of reliability of the compressor is increased, but also since all the sliding parts of the compression member P are immersed in the oil, the efficiency of the compressor can be improved by the sealing effect of the oil.

Fig. 5 shows a rotary compressor mounted in a split type air conditioner for cooling and heating, and compares the temperature distribution inside the compressor when the winding cover 30 is present during the heating operation. Further, in order to reduce the heat loss during the heating operation, the outer circumference of the casing 2 is covered with a heat insulating material. 5, the muffler vent hole of the exhaust muffler 55 that communicates with the vent hole 54 of the compression member P is bored in the winding cover 30. The TS of the horizontal axis is the temperature of the suction refrigerant of the cylinder 51, Tdl is the temperature of the refrigerant discharged from the exhaust muffler 55, Tml and Tm2 are the temperatures of the winding end portion 15a and the winding end portion 15b, respectively, and Td2 is the exhaust pipe 3 The temperature of the discharged refrigerant, Toi l is the oil temperature of the oil reservoir F. In addition, the vertical axis shows the temperature (°C) of the above components.

In the state without the winding cover (symbol N, - -〇- - ), most of the high-pressure refrigerant (Tdl) discharged from the exhaust muffler 55 comes into contact with the winding end face 15a, and the helium returns to less gas resistance. The direction of the core slit 13 is passed from the lower portion of the core slit 13 to the upper portion, and moved to the oil separation chamber T. At the same time, the residual refrigerant passes through the gap between the motor winding 15 and the winding around which the gas resistance is large, and moves to the oil separation chamber Τ. The two high-pressure refrigerants after the split are discharged from the exhaust pipe 3 after being merged in the oil separation chamber. On the other hand, in the state in which the winding cover is provided (marks ¥, -· - ), as described above, all the high-pressure refrigerant discharged from the exhaust muffler 55 passes through the gap between the motor winding 15 and the winding, and is moved to the oil. Separate the cavity. Thereafter, it is discharged from the exhaust pipe 3.

The winding end face temperature is compared by the presence or absence of a winding cover. Due to the cooling effect of the discharge refrigerant (Tdl), the temperature of the winding end portion 15a (Tml) and the winding end portion 15b (Tm2) is lower when there is a winding cover, and the maximum temperature of the winding end portion 15b (Tm2) is about 10 The difference between °C. On the other hand, when the discharge temperature (Td2) has a winding cover, the temperature becomes high, and the temperature difference from the winding-free cover is about 12 °C.

Moreover, the oil temperature (Toi l ) of the oil reservoir F also produces a significant difference. When there is a winding cover, it is about 14 °C higher than the windingless cover. The reason for this is that there is no heat exchange with the discharge refrigerant (Tdl) when there is a winding cover; the principle that the oil in the oil reservoir is directly cooled by the discharge refrigerant (Tdl) when there is no winding cover. In the state with the winding cover, the oil temperature of the oil reservoir F is probably determined by the oil falling from the oil separation chamber T.

As can be seen from Figure 5, due to the winding cover 30, the motor winding temperature is lowered, the exhaust gas temperature and the oil temperature are increasing. When the motor winding temperature is lowered, the motor failure rate is lowered and the motor efficiency is improved. The increase of the exhaust gas temperature will increase the heating comfort and the hot water temperature increase, and the oil temperature increase. Prevents the effect of oil viscosity reduction due to a decrease in oil superheat.

Next, a method of further realizing the effect of the first embodiment by a small design improvement will be described based on Fig. 6 . The rotary compression member P is composed of a cylinder 51, a main bearing bearing 53 and a sub-bearing 57 assembled on the upper and lower surfaces, a piston 63 and a sliding plate 64 provided on the compression chamber 52, and an eccentric operating piston 63. The main bearing 53 and the sub-bearing 57 are configured by a crankshaft 60 that slidably supports.

Therefore, the slider chamber 67 is semi-closed by blocking the upper cover 68a and the lower cover 68b at the upper and lower opening portions of the slider chamber 67 formed at the back of the slider 64 of the air cylinder 51, respectively. The upper cover 68a and the lower cover 68b are intended to prevent oil agitation of the oil reservoir F caused by the reciprocating motion of the slider 64, thereby achieving the effect of stabilizing the oil level. Further, the oil supply hole 69 in the lower cover 68b supplies oil to the slider chamber 67. Further, in the state where the oil reservoir chamber F is opened, the opening portion of the slider spring hole 65 can be blocked by a plate including the upper cover 68a and the lower cover 68b.

In Fig. 6, the upper end of the oil groove 60a of the crankshaft 60 is designed to be not open in the winding cover 30. Through this setting Since the oil discharged from the inner diameter of the crankshaft 60 flows downward from the upper portion of the main bearing 53, the supplied oil does not flow into the winding cover 30. Therefore, the oil flowing into the oil separation chamber is only mixed with the oil discharged from the compression chamber 52, and the amount of oil discharged from the exhaust pipe 3 is reduced.

Fig. 7 shows an application design example of the first embodiment, even if the exhaust pipe 3 is disposed to open to the oil passage S. In this design, the refrigerant separated in the oil in the oil separation chamber T flows from the upper end of the oil passage S in which the exhaust pipe 3 is disposed to the opening of the exhaust pipe 3. On the other hand, most of the oil separated in the oil separation chamber T is dropped from the three oil passages S of the exhaust pipe 3 to the oil reservoir F. However, since some of them are discharged from the exhaust pipe 3 by mixing with the refrigerant, there is a slight increase in the amount of oil discharged. However, compared with the conventional design, the amount of oil discharged is greatly reduced.

Figures 8 and 9 are alternative designs of the oil passage S. In Fig. 8, a plurality of stator through holes 14 penetrating the upper and lower sides of the stator core 12 are provided between the outer circumference of the stator core 12 and the motor winding 15. The stator through hole 14 serves as an alternative means for the oil drop passage S. Figure 9. A bypass pipe 90 opening in the oil separation chamber T and the oil reservoir F is provided outside the casing 2. This bypass pipe 90 serves as an alternative to the oil passage S.

Next, the material of the winding cover 30 will be described. The winding cover 30 is formed of a synthetic resin material which can achieve electrical insulation, refrigerant resistance, oil resistance, heat resistance and the like. For example, PBT (thermoplastic saturated polyester) used in the motor winding insulation frame of a concentrated winding motor or the like can be borrowed. This material allows contact with the motor windings 15. In addition, even a metal material such as a steel plate can be used if the motor winding is insulated or a certain gap is ensured between the motor winding and the motor winding. Embodiment 2,

The embodiment 2 shown in Fig. 10 is for miniaturizing the winding cover 30 employed in the first embodiment, and further, it is intended to increase the volume of the oil reservoir F. The compression member P in the second embodiment is a rotation type composed of a double cylinder. Further, the outer diameter of the flange of the main bearing 53 is fixed to the inner wall of the casing 2. The motor M uses a variable frequency motor in which the motor winding 15 is a concentrated winding method.

A circular hole formed in the center of the bowl-shaped winding cover 30 having a small upper and lower width is fitted to the outer diameter of the muffler exhaust port 56 which is opened along the hub of the main bearing 53. Further, since the inner diameter of the outer peripheral frame of the winding cover 30 is fitted to the outer diameter of the winding insulating frame 17 of the motor M, the winding end face 15a is covered with the winding cover 30. A second spring 41 provided between the bottom surface of the winding cover 30 and the upper surface of the exhaust muffler 55 presses the winding cover 30 toward the stator core 12 to prevent vibration of the winding cover 30. However, in a state where the winding cover 30 is fixed to the winding insulating frame 17, the second spring 41 can be omitted.

In the second embodiment, the high-pressure refrigerant discharged from the twin cylinders merges in the exhaust muffler 55, passes through the muffler exhaust port 56, and flows into the inside of the winding cover 30. Thereafter, as in the first embodiment, after the high-pressure refrigerant is heat-exchanged with the motor winding 15, Flow to the oil separation chamber τ.

In the second embodiment, by connecting the exhaust muffler 55 and the winding cover 30 in series, and in the motor winding, a centralized winding method is adopted, it is possible to achieve miniaturization of the winding cover 30 and enlarge the oil reservoir F. Volume. Further, as shown in Embodiment 2, the winding cover 30 is applicable to a multi-cylinder rotary compressor and a variable frequency motor. Further, as shown in Fig. 6 of the first embodiment, the slider chamber (not shown) disposed in the double cylinder is semi-closed, and oil agitation due to the slider to the oil reservoir F can be prevented.

Further, in the two-cylinder rotary compressor, since the balance block (not shown) fixed to the rotor 20 of the motor is small and the winding end portion 15 of the concentrated winding type is small, the miniaturization of the winding cover 30 is facilitated. In addition, it is characterized by a concentrated winding method that expands the refrigerant passage inside the motor.

The embodiment 2 shown in Fig. 1 is an application design example of Fig. 10, and the exhaust muffler is connected through the communication pipe 32.

55 and winding cover 30. Therefore, the high-pressure refrigerant discharged from the compression member Ρ to the exhaust muffler 55 flows from the communication pipe 32 through the winding cover 30 to the oil separation chamber 内部 from the inside of the motor Μ.

In this design example, the oil discharged from the upper end of the oil groove 53a of the main bearing 53 directly merges with the oil of the oil reservoir F. Therefore, it is found that the oil amount of the oil storage chamber F changes little, and the discharge amount of the exhaust pipe 3 is less. As shown in the second embodiment, a new effect can be obtained by the exhaust passage and the winding cover 30 which are connected to the compression member P in the communication pipe 32.

The right side of Fig. 11 shows the details of the winding cover 30 and the connecting pipe 32 connecting the winding cover 30. The shaft hole 62 provided in the center of the winding cover 30 has a hole penetrating the crankshaft 60 and a slight gap between the outer diameter of the crankshaft 60 for sliding. Further, even if the connecting pipe 32 and the winding cover 30 are integrally formed, it is possible to easily connect with the exhaust muffler 55 if there is another elastic pipe member. Embodiment 3,

The housing is used as a rotary compressor RC on the high pressure side, because there is a reservoir A on the suction circuit, usually, the compression chamber

52 will avoid excessive refrigerant inhalation. However, when starting and defrosting operation, over-sealing of the refrigerant, etc., a large amount of liquid refrigerant temporarily flows into the compression chamber 52, and the amount of discharged refrigerant is abnormally increased. Similarly, in a large-scale rotary compressor type variable-speed compressor, the amount of continuous refrigerant discharged is maximized during high-speed operation. Under such operating conditions, vibration and looseness of the winding cover 30 may occur due to the large amount of refrigerant passing through the winding cover 30.

As a countermeasure against the above problem, in the third embodiment shown in FIG. 12, the bypass hole 33 is added to the upper portion of the winding cover 30, and a part of the discharge refrigerant escapes to the outside of the winding cover 30, thereby reducing the winding cover 30 to the motor M. The amount of refrigerant inside. The refrigerant that has flowed out of the outside of the winding cover 30 passes through the oil passage S, flows to the oil separation chamber T, and merges with the refrigerant passing through the inner diameter surface of the motor bore. During this period, the amount of oil falling from the oil separation chamber to the oil reservoir F is reduced, and the amount of oil discharged from the exhaust pipe 3 is increased. Here, the ratio of the amount of refrigerant flowing from the winding 30 to the oil separation chamber T after passing through the inside of the motor M and the amount of refrigerant flowing from the bypass hole 33 through the oil passage S into the oil separation chamber is 8:2. On the other hand, in the state without the winding cover 30, that is, in the conventional design, since the above ratio is considered to be about 4: 6, the refrigerant flowing from the oil passage S into the oil separation chamber is affected by the presence or absence of the winding cover 30. The ratio of the quantity is Q . 25: 1. 5 0 or 1: 6.

Therefore, in the third embodiment having the bypass hole 33, the amount of refrigerant flowing from the oil passage S into the oil separation chamber is less overwhelming, and thus it is advantageous to increase the amount of oil discharged. As a result, it is allowed to increase the number and area of the bypass holes 33 if necessary. That is to say, the cavity formed by the winding cover 30 is not closed, even a semi-closed cavity.

Here, in the design in which the bypass hole 33 is added to the winding cover 30, the bypass hole 33 can be opened only when the amount of discharged refrigerant is excessively large. Therefore, when the amount of the discharged refrigerant is exceeded, the bypass hole 33 is opened, and when the set value or lower is reached, the bypass hole 33 is closed, which is convenient.

When the right side of Fig. 12 is shown, a simple differential pressure valve 37 is added, and a pressure difference between the internal pressure of the winding cover 30 and the outer pressure of the winding cover 30 (same as the oil reservoir F) is passed, and the differential pressure valve is passed. 37 means for opening and closing the through hole 33 to achieve the above purpose. Since the internal pressure of the winding cover 30 is increased because the amount of discharged refrigerant is excessively large, the differential pressure valve 37 is opened to discharge excess refrigerant. However, if the internal pressure is reduced, since the differential pressure valve 37 is closed, the discharge is stopped. Further, in the third embodiment, the differential pressure valve 37 is a reed valve composed of the main valve 37a and the auxiliary valve 37b, and is fixed to the side wall of the winding cover 30. Embodiment 4,

The embodiment 3 shown in Fig. 13 is characterized in that an additional auxiliary winding cover 44 surrounds the winding end face 15b. The right side of Figure 13 shows the details of the auxiliary winding cover 44. The auxiliary winding cover 44 is a bowl-shaped cover, and the outer circumference is provided with a plurality of outer peripheral holes 4 and two auxiliary projections 35b, and a vent hole 44b provided in the center portion. Alternatively, the auxiliary winding cover 44 may use a material similar to the winding cover 30.

In Fig. 13, as in the winding cover 30 of the first embodiment, the winding end faces 15b are surrounded by the auxiliary winding cover 44, and the two auxiliary projections 35b are fitted into the core groove 13a.

Optionally, the housing 2 comprises: an upper housing 2£1 and a lower housing 2b, the upper housing 2a being connected to the exhaust pipe 3, the upper housing

A coil spring 45 provided in the vertical direction is provided on the lower surface of 2a. The lower casing 2b is connected below the upper casing 2a, wherein the motor ^ compression means? The winding cover 30 and the auxiliary winding cover 44 are both disposed in the lower casing 2b, wherein the lower end of the coil spring 45 abuts against the upper surface of the auxiliary winding cover 44) and is positioned corresponding to the vent hole 44b.

Thus, the upper casing 2a, in which the coil spring 45 has been previously disposed, is inserted into the lower casing 2b, and the auxiliary winding cover 44 is pressed against the coil spring 45 to be fixed to the upper surface of the stator 11. At this time, all of the winding end faces 15b are covered by the auxiliary winding cover 44. The plurality of outer peripheral holes 44a are oil vent holes, and are opened on the outer circumference of the winding end surface 15b. Further, the exhaust hole 44b corresponds to the inner diameter of the coil spring 45. As in the first embodiment, the mixed refrigerant including the oil discharged from the exhaust port 54 of the compression member flows out of the auxiliary winding cover 44 while cooling the motor winding 15 through the winding cover 30. Here, a large mass of oil splashes on the inner circumference of the auxiliary winding cover 44, and the plurality of outer peripheral holes 44a fall toward the oil passage S. On the other hand, the refrigerant having a small mass passes through the gap between the upper surface of the circular plate 70 and the auxiliary winding cover 44, and is discharged from the exhaust hole 44b to the exhaust pipe 3, and then discharged to the condenser C. The oil remaining in the discharge refrigerant first slides over the auxiliary winding cover 44 to the oil passage S before flowing into the exhaust pipe 3.

As described, the auxiliary winding cover 44 can not only further increase the oil separation effect, reduce the amount of oil discharged to the refrigerant circulation device, but also reduce the temperature of the winding portion 15b which is most susceptible to heat.

It should be noted that regarding the utilization possibilities of the industry:

According to the rotary compressor of the embodiment of the present invention, it is necessary to add the winding cover 30, but the conventional design such as the compression member, the motor, and the casing 2 in the main parts can be borrowed, and the mass productivity is good. Further, the present invention can be widely applied to rotary compressors such as vertical rotary compressors and scroll compressors, and applications such as air conditioners, refrigeration equipment, and CO2 water heaters in which the compressors are mounted. In addition, the greenhouse gasification coefficient (GWP) is low, and it is planned that the new refrigerant, such as an air conditioner, will be included in the planned refrigerant R32, and the operating temperature is higher than that of the conventional refrigerant. The application of the present invention makes it easier to solve the problem. .

Other configurations of the rotary compressor according to embodiments of the present invention, such as compression devices and the like, and operations are known to those skilled in the art and will not be described in detail herein. A refrigeration cycle apparatus according to an embodiment of the second aspect of the present invention, comprising: a rotary compressor, a condenser (:, an evaporator E, an expansion device V, and a reservoir according to an embodiment of the first aspect of the present invention. As shown in Fig. 15, the condenser C is connected to the exhaust pipe 3 in the rotary compressor, and the evaporator is connected to the condenser through the expansion device V. Alternatively, the expansion device V is an expansion valve. The reservoir A is connected to the evaporation. The device E is between the suction pipe 9 and the compression chamber 52.

The refrigeration cycle apparatus according to an embodiment of the present invention further includes: a refrigerant injection pipe 80 having one end connected to the connection passage of the condenser C and the expansion device V and the other end connected to the flange side of the sub-bearing 57 and It is in communication with the compression chamber 52. Optionally, a flow regulating valve 86 is disposed on the refrigerant injection pipe 80. Further, the refrigeration cycle device further includes: a temperature sensor 85 and a control device 87. As shown in Fig. 14, the temperature sensor 85 is connected to the exhaust pipe 3, and the control device 87 is connected to the temperature sensor 85.

A refrigeration cycle apparatus according to an embodiment of the present invention will be specifically described below with reference to Figs.

Embodiment 5,

The compression load of the rotary compressor fluctuates with changes in the ambient temperature. In the overload conditions of the cooling and heating operation, the motor winding temperature exceeds the safety limit. In order to solve this problem, in the fifth embodiment, the motor winding is directly cooled by the discharge refrigerant in the compression member by the features of the present invention. To this end, the liquid refrigerant injection system It is applied to the rotary compressor RC to improve the motor winding cooling efficiency and motor temperature control. Embodiment 5 shown in Fig. 14 shows a method of connecting both ends of the refrigerant injection pipe 80 between the condenser C and the expansion valve V, and the sub-bearing 57 in the refrigeration cycle apparatus including the rotary compressor RC. Lan side. Further, a flow rate adjusting valve 86 and a temperature sensor 85 fixed to the exhaust pipe 3 are connected to the control unit 87 in the middle of the refrigerant injection pipe 80. Further, the refrigerant injection hole 81 provided in the sub-bearing 57 is opened in the compression chamber 52.

Due to the liquid refrigerant injected into the compression chamber 52 after passing through the flow regulating valve 86, the temperature-reducing refrigerant can directly cool the motor winding 15 through the winding cover 30. That is, the liquid refrigerant injected into the compression chamber 52, the oil 6 that does not cool the reservoir T, and the stator core 12 are used for cooling the motor winding 15. Therefore, compared with the conventional compressor, a high-efficiency cooling effect can be achieved with a small amount of liquid refrigerant. In other words, it is possible to prevent an increase in electrical consumption due to excessive injection of refrigerant. In addition, since there is no cooling oil 6, there is no problem that the degree of superheat of the oil is lowered.

Further, as illustrated in Fig. 5, the present embodiment is characterized in that the discharge refrigerant temperature is close to the maximum temperature of the motor winding. Therefore, the temperature of the exhaust pipe 3 is monitored by the temperature sensor 85, thereby adjusting the opening degree of the flow regulating valve 86, and the temperature of the motor winding 15 can be appropriately controlled. Further, the same action and effect can be obtained by the gas refrigerant injection technique of the fifth embodiment for the purpose of improving the efficiency of the refrigeration cycle apparatus. Further, the flow rate adjusting valve 86 and the temperature sensor 85 can be omitted in a state where the motor winding 15 is not required to be closely controlled. Embodiment 6,

For example, Japanese Patent Laid-Open No. Hei 9-217692 (JP-A-1997-217692), "Compressor-Coiled Scroll Compressor", the internal scroll pressure as a high-pressure side vertical scroll compressor and rotary pressure The same problem exists in the shrinking machine. The embodiment 6 shown in Fig. 15 solves the problems of the scroll compressor by applying the techniques disclosed in the first to the fifth embodiments.

The vertical scroll compressor SC of the sixth embodiment is assembled by a compression member P assembled on the inner circumference of the sealed cylindrical casing 2, a motor M disposed on the upper side, and a lower end of the stator 11. The winding cover 30 and the like are configured to enclose the oil 6 in the oil reservoir F of the casing 2.

The low-pressure refrigerant sucked into the suction pipe 9 of the stationary plate 95 is compressed by the movable plate (not shown) which is eccentrically operated in the stationary plate 95, and is compressed to become an oil-containing high-pressure mixed refrigerant, which is discharged into the winding cover 30. Since the flow of the mixed refrigerant thereafter is the same as that of the first embodiment, the winding cover 30 brings about the same action and effect, and therefore the description thereof will be omitted. Therefore, the present invention is not limited to the rotary compressor and the scroll compressor, and may be applied to a vertical rotary compressor in which the internal pressure of the casing is used as the high pressure side.

In the description of the present specification, the description of the terms "one embodiment", "some embodiments", "illustrative embodiment", "example", "specific example", or "some examples", etc. Particular features, structures, materials or features described in the examples or examples are included in at least one embodiment or example of the invention. In the present specification, the schematic representation of the above terms does not necessarily mean the same embodiment or example. Moreover, the specific features, structures, materials or The features may be combined in any suitable manner in any one or more embodiments or examples.

While the embodiments of the present invention have been shown and described, the embodiments of the invention may The scope of the invention is defined by the claims and their equivalents.

Claims

claims

1. A rotary compressor, characterized in that it includes:

A sealed housing (2) equipped with an exhaust pipe (3), and the lower part of the housing has an oil storage chamber (F) for storing lubricating oil;

Motor (M), the motor is located in the housing, the motor includes a stator (11) with a motor winding (15) and a rotor (20) nested inside the stator, the outer peripheral wall of the stator and There is a gap between the inner walls of the housing, and there is an oil separation chamber (T) above the motor in the housing;

Compression device (P), the compression device is located on the lower side of the motor and includes a crankshaft (60), a main bearing (53), an auxiliary bearing (57) and a bearing between the main bearing and the auxiliary bearing. Cylinder (51), a compression chamber (52) is defined between the main bearing, the auxiliary bearing and the cylinder;

Winding cover (30), the winding cover is located between the stator and the compression device and surrounds the lower end of the motor winding, wherein the oil-containing high-pressure refrigerant discharged from the compression chamber is discharged from the compression chamber. The winding cover flows through the motor to the oil separation chamber;

The outside of the winding cover has an oil channel (S) that communicates with the oil storage chamber (F) and the oil separation chamber (T).

2. The rotary compressor according to claim 1, characterized in that the exhaust pipe is connected to the housing at the oil separation chamber or the oil passage.

3. The rotary compressor according to claim 1, characterized in that the oil passage (S) is jointly defined by the outside of the winding cover and the gap between the stator and the casing.

4. The rotary compressor according to claim 1, characterized in that the oil passage (S) is composed of a pipe provided outside the housing, and both ends of the pipe are connected to the oil storage respectively. chamber and the oil separation chamber.

5. The rotary compressor according to any one of claims 1 to 4, characterized in that the winding cover includes: a first column section (301), the upper end of the first column section is sleeved on the outside the stator;

Second column section (302), the second column section is located below the first column section, and the inner diameter of the second column section is smaller than the inner diameter of the first column section, the second column section Sleeved outside the upper end of the main bearing (53) of the compression device; and

Connecting section (303), the connecting section is in the shape of an inverted truncated cone and is connected between the first column section and the second column section.

6. The rotary compressor according to claim 5, characterized in that a plurality of iron core cutouts (13) are formed on the outer peripheral wall of the stator, and each of the iron core cutouts is formed by cutting the outer circumference of the stator. It is formed by cutting off a part, and the plurality of iron core cutouts penetrates the axial direction of the stator, and the gap is formed between the outer peripheral wall of the stator and the inner wall of the housing through the iron core cutouts.

7. The rotary compressor according to claim 6, characterized in that the plurality of iron core incisions of the stator are respectively recessed inward to form iron core grooves (13a), and the iron core grooves penetrate through all the iron core grooves. Describe the axial direction of the stator;

A plurality of protrusions (35) extend upward from the outer side of the upper end of the first column section of the winding cover. The number of the protrusions is less than the number of the iron core slots, and each of the protrusions is embedded in a corresponding iron core slot. the lower end of the winding cover to match the upper end of the winding cover with the stator.

8. The rotary compressor according to claim 7, wherein a flange (304) extends outward from the lower end of the second column section of the winding cover;

The rotary compressor further includes a spring (40). Both ends of the spring are respectively stopped against the lower surface of the flange and the upper surface of the cylinder to stop the upper end surface of the first column section. against the lower surface of the stator.

9. The rotary compressor according to claim 7, wherein the iron core cutouts include four and are evenly distributed along the circumferential direction, and the protrusions are two opposite ones.

10. The rotary compressor according to claim 9, further comprising:

Auxiliary winding cover (44), the auxiliary winding cover is located above the motor and surrounds the upper end of the motor winding. The peripheral wall of the auxiliary winding cover has a plurality of peripheral holes (44a), and a row of holes is formed in the center. Stomata (44b).

11. The rotary compressor according to claim 10, wherein the auxiliary winding cover (44) is formed into an inverted bowl-shaped structure, and the lower end of the auxiliary winding cover (44) extends downwardly. Two auxiliary protrusions (35b) are formed, and the two auxiliary protrusions (35b) are embedded in the upper ends of corresponding core slots to match the lower end of the auxiliary winding cover (44) with the stator.

12. The rotary compressor according to claim 11, characterized in that the housing (2) includes: an upper housing (2a), the upper housing is connected to the exhaust pipe, and the upper housing (2a) is connected to the exhaust pipe. The lower surface of the housing is provided with coil springs (45) arranged in the up and down directions;

Lower housing (2b), the lower housing is connected below the upper housing, wherein the motor (M), the compression device (P), the winding cover (30) and the auxiliary The winding covers (44) are all arranged in the lower housing, wherein the lower end of the coil spring stops on the upper surface of the auxiliary winding cover (44) and the position corresponds to the exhaust hole (44b).

13. The rotary compressor according to claim 5, characterized in that the upper end of the crankshaft is provided with a circular plate (70) coaxially arranged therewith.

14. The rotary compressor according to claim 5, characterized in that the upper side wall of the winding cover has a bypass hole (33) penetrating therethrough.

15. The rotary compressor according to claim 14, characterized in that a differential pressure valve (37) is further provided on the winding cover, and the differential pressure valve is arranged corresponding to the bypass hole to adjust the pressure according to the bypass hole. The pressure difference between the inside and outside of the winding cover opens or closes the bypass hole.

16. The rotary compressor according to claim 15, characterized in that the pressure difference valve is a reed valve and includes a main valve (37a) and an auxiliary valve (37b) fixed on the outer wall of the winding cover. ).

17. The rotary compressor according to any one of claims 1 to 4, characterized in that the motor winding (15) used in the motor is a variable frequency motor with a concentrated winding method.

18. The rotary compressor according to claim 17, further comprising: an exhaust silencer (55) located between the motor and the main bearing, the exhaust silencer having a silencer Exhaust port (56), the muffler exhaust port (56) is sleeved on the hub of the main bearing;

There are two cylinders in the compression device, and the flange outer diameter of the main bearing (53) is fixed on the inner wall of the housing (2).

19. The rotary compressor according to claim 18, characterized in that the winding cover (30) is formed into a bowl-shaped structure and has a circular hole formed in the center, and the circular hole is connected to the exhaust gas of the muffler. The outer diameter of the opening (56) is fitted; the motor M has a winding insulation frame (17) located outside the winding, wherein the inner diameter of the winding cover (30) is fitted with the winding insulation frame (17) So that the lower end of the motor winding is covered by the winding cover (30).

20. The rotary compressor according to claim 19, characterized in that, the rotary compressor further includes a second spring (41), the second spring is stopped against the lower surface and row of the winding cover. between the upper surfaces of the gas silencer (55).

21. The rotary compressor according to claim 5, characterized in that the winding cover is made of non-conductive material or a material that has undergone non-conductive treatment.

22. A refrigeration cycle device, characterized in that it includes:

A rotary compressor according to any one of claims 1-21;

A condenser (C) connected to the exhaust pipe (3) in the rotary compressor;

Evaporator (E), the evaporator is connected to the condenser through an expansion device (V);

Liquid reservoir (A), the liquid reservoir is connected between the evaporator (E) and the suction pipe (9) communicated with the compression chamber (52).

23. The refrigeration cycle device according to claim 22, further comprising: a refrigerant injection pipe (80), one end of the refrigerant injection pipe is connected to the connecting passage between the condenser and the expansion device, and The other end is connected to the flange side of the auxiliary bearing (57) and communicates with the compression chamber (52).

24. The refrigeration cycle device according to claim 23, characterized in that the refrigerant injection pipe (80) is provided with a flow adjustment valve (86).

25. The refrigeration cycle device according to claim 23, further comprising:

Temperature sensor (85), the temperature sensor (85) is connected to the exhaust pipe (3);

Control device (87), the control device is connected to the temperature sensor.