CN204436789U - Rotary compressor - Google Patents

Abstract

The utility model discloses a rotary compressor, comprising: a casing and a compression mechanism, the casing has an oil pool, the compression mechanism includes two supporting parts, a cylinder, a piston, a sliding plate and a crankshaft, and the two supporting parts are arranged on the cylinder A compression chamber is defined between the axial ends of the cylinder and the cylinder. The piston is sleeved on the crankshaft and located in the compression chamber. A slide groove communicating with the compression chamber is formed on the cylinder, and the slide is movably arranged in the slide groove. inside, and the tip of the sliding plate abuts against the outer peripheral wall of the piston to separate the compression chamber into a suction chamber and an exhaust chamber, at least one of the two support members is formed with an oil hole, and the lubricating oil in the oil pool is suitable for passing through The oil hole enters into the exhaust chamber to lubricate the tip of the slide, wherein when the length of the slide into the compression chamber is the longest, the tip of the slide covers at least part of the oil hole. According to the rotary compressor of the utility model, the oil hole is provided on the supporting member, thereby improving the lubrication condition of the tip of the sliding vane and improving the reliability.

Description

rotary compressor

technical field

The utility model relates to the field of compressor equipment, in particular to a rotary compressor.

Background technique

It is pointed out in the related art that the reliability of the rotary compressor is the key factor affecting the life of the product. Good lubrication between the moving pairs in the rotary compressor is the premise to ensure the reliability of the rotary compressor. However, the rotary compressor In the compression mechanism of the compressor, the kinematic pair between the sliding vane and the piston is often in a state of boundary lubrication, and the tip of the sliding vane is easy to wear, which leads to the performance degradation or even failure of the rotary compressor.

Utility model content

The utility model aims at at least solving one of the technical problems existing in the prior art. To this end, the utility model is to provide a rotary compressor, which improves the lubrication condition of the tip of the sliding vane.

According to the utility model, the rotary compressor includes: a casing with an oil pool inside; and a compression mechanism, which includes two supports, a cylinder, a piston, a sliding vane and a crankshaft, the two The bearings are arranged at both axial ends of the cylinder to define a compression chamber with the cylinder, the lower end of the crankshaft passes through the two bearings and the cylinder, and the piston is sleeved on the cylinder. On the crankshaft and located in the compression chamber, a slide groove communicating with the compression chamber is formed on the cylinder, the slide is movably arranged in the slide groove, and the tip of the slide It abuts against the outer peripheral wall of the piston to divide the compression chamber into an air suction chamber and an exhaust chamber, at least one of the two support members is formed with an oil hole, and the lubricating oil in the oil pool is suitable for Into the exhaust chamber through the oil hole to lubricate the tip of the slide, wherein the tip of the slide is longest when the length of the slide into the compression chamber is the longest Covering at least part of the oil hole.

According to the rotary compressor of the utility model, oil holes are provided on the supporting member to provide lubricating oil to the tip of the sliding vane, thereby improving the lubrication of the tip of the sliding vane, reducing the wear of the tip of the sliding vane, and improving the Operating reliability of rotary compressors.

Specifically, when the length of the sliding vane protruding into the compression chamber is the longest, on the horizontal plane perpendicular to the axial direction of the cylinder, the end of the oil hole far away from the sliding vane groove and the piston The outer peripheral wall is in contact with or covered by the piston.

Optionally, the oil hole extends radially of the cylinder and is parallel to the sliding plate.

Further, the side wall of the oil hole away from the air suction chamber is flush with the side wall of the slide plate away from the air suction chamber.

Specifically, the length L of the oil hole in a direction parallel to the movement of the sliding vane satisfies: Wherein, 90°≤θ≤270°, wherein, e is the eccentricity of the crankshaft, and r is the radius of the outer edge of the piston.

Specifically, the width D of the oil hole in the direction perpendicular to the movement of the slide meets: Wherein, D _is the thickness of the slide.

Further, the rotary compressor further includes: an oil pipe, the oil pipe is arranged on the at least one of the two support members, and one end of the oil pipe communicates with the oil hole, and the oil pipe The other end is immersed in the oil pool.

Specifically, the angle α between the centerline of the oil pipe and the central axis of the cylinder satisfies: 0≤α<90°

Further, the cylinder has a suction hole communicating with the suction cavity, wherein the other end of the oil pipe is opposite to the central axis of the suction hole in the axial direction of the cylinder.

Optionally, the oil hole is a circular hole, an oval hole, an oblong hole or a polygonal hole.

Optionally, there is one cylinder, and the two supports are a main bearing and an auxiliary bearing.

Optionally, there are multiple cylinders, a partition is provided between every two adjacent cylinders, and at least one of the two supporting members is the partition.

Additional aspects and advantages of the invention will be set forth in the description which follows, and in part will be obvious from the description, or may be learned by practice of the invention.

Description of drawings

Fig. 1 is a schematic cross-sectional view of a rotary compressor according to an embodiment of the present invention;

Fig. 2 is a top view of the rotary compressor shown in Fig. 1;

Fig. 3 is a sectional view along line A-A in Fig. 2;

Fig. 4 is a working schematic diagram of the piston shown in Fig. 3;

Fig. 5 is a top view of the auxiliary bearing shown in Fig. 3;

Fig. 6 is a sectional view along the line B-B in Fig. 5;

Fig. 7 is a schematic diagram of the working state of the compression mechanism shown in Fig. 3;

Fig. 8 is a schematic diagram of a working state of the compression mechanism shown in Fig. 7;

Fig. 9 is an enlarged view of part C circled in Fig. 8;

Fig. 10 is a schematic diagram of another working state of the compression mechanism shown in Fig. 7;

Fig. 11 is an enlarged view of part D circled in Fig. 10;

Fig. 12 is another schematic diagram of the working state of the compression mechanism shown in Fig. 7;

Fig. 13 is an enlarged view of part E circled in Fig. 12 .

Reference signs:

100: rotary compressor;

1: Shell;

2: motor; 21: rotor; 22: stator;

3: compression mechanism; 311: main bearing; 312: auxiliary bearing; 313: oil hole; 314: oil pipe;

    32: Cylinder; 321: Compression cavity; 3211: Suction cavity; 3212: Exhaust cavity;

33: Piston; 34: Slider;

35: crankshaft; 351: eccentric part;

200: liquid reservoir; 201: suction tube assembly; 2011: catheter; 2012: tapered tube.

Detailed ways

Embodiments of the present invention are described in detail below, examples of which are shown in the drawings, wherein the same or similar reference numerals represent the same or similar elements or elements having the same or similar functions throughout. The embodiments described below by referring to the figures are exemplary and are intended to explain the present invention, but should not be construed as limiting the present invention.

The following disclosure provides many different embodiments or examples for realizing different structures of the present invention. To simplify the disclosure of the present invention, components and arrangements of specific examples are described below. Of course, they are only examples, and the purpose is not to limit the utility model. Furthermore, the present invention may repeat reference numerals and/or letters in different instances. This repetition is for the purpose of simplicity and clarity and does not in itself indicate a relationship between the various embodiments and/or arrangements discussed. In addition, various specific process and material examples are provided herein, but one of ordinary skill in the art will recognize the applicability of other processes and/or the use of other materials.

The following describes a rotary compressor 100 according to an embodiment of the present invention with reference to FIGS. 1-13 . Wherein, the rotary compressor 100 may be a vertical compressor or a horizontal compressor, and the following only takes the rotary compressor 100 as a vertical compressor as an example for illustration.

As shown in FIG. 1 , a rotary compressor 100 according to an embodiment of the present invention includes: a housing 1 , a compression mechanism 3 , a motor 2 and the like.

Referring to Fig. 1, the casing 1 can be generally formed as a cylindrical airtight container, and the motor 2 and the compression mechanism 3 are all arranged in the casing 1, wherein the motor 2 can include a rotor 21 and a stator 22, and the compression mechanism 3 can include a crankshaft 35 and the compression assembly, the motor 2 and the compression assembly are spaced apart in the axial direction of the housing 1, one end of the crankshaft 35 is fixed to the rotor 21, and the other end of the crankshaft 35 runs through the compression assembly, so that when the motor 2 is working, it can pass The rotor 21 drives the crankshaft 35 to rotate to compress the refrigerant in the compression assembly.

Specifically, the compression assembly may include two supports (such as the main bearing 311, the sub-bearing 312 or the separator described below) and the cylinder 32. A compression chamber 321 is defined therebetween. Here, it should be noted that the rotary compressor 100 can be a single-cylinder compressor or a multi-cylinder compressor. When the rotary compressor 100 is a single-cylinder compressor (as shown in FIG. 1 ), there is one cylinder 32, and the cylinder The two supporting members at both axial ends of 32 are the main bearing 311 and the auxiliary bearing 312 respectively. When the rotary compressor 100 is a multi-cylinder compressor (not shown in the figure), there are multiple cylinders 32, and the multiple cylinders 32 are arranged at intervals in the axial direction, and each adjacent two cylinders 32 are provided with A partition, at least one of the two supports is a partition.

Specifically, when the multi-cylinder compressor is a double-cylinder compressor, there are two cylinders 32, a partition is provided between the two cylinders 32, and the other end of one cylinder 32 is provided with a main bearing 311. At this time, the cylinder 32 The two supports at both ends of the axial direction are respectively the main bearing 311 and the partition, and the other end of the other cylinder 32 is provided with a secondary bearing 312. At this time, the two supports at the axial ends of the cylinder 32 are respectively the secondary bearing 312 and the partition plate.

Further, when the multi-cylinder compressor is a three-cylinder compressor, there are three cylinders 32, and the three cylinders 32 are arranged at intervals in the axial direction, and a partition is provided between every two adjacent cylinders 32, and the One end of the two cylinders 32 away from the middle cylinder 32 is respectively provided with a main bearing 311 and an auxiliary bearing 312, wherein the two supports at the two axial ends of the cylinder 32 adjacent to the main bearing 311 are respectively the main bearing 311 and the separator, adjacent to the main bearing 311. The two supports at the axial ends of the cylinder 32 provided by the auxiliary bearing 312 are respectively the auxiliary bearing 312 and the partition, and the two supports at the axial ends of the intermediate cylinder 32 are both partitions.

Here, it should be noted that the structures of other multi-cylinder compressors can be deduced in the same way, so details will not be repeated one by one. The following only takes the rotary compressor 100 as an example of a single-cylinder compressor for illustration. Those skilled in the art can obviously understand the technical solution that the rotary compressor 100 is a multi-cylinder compressor after reading the following technical solutions.

Specifically, as shown in FIGS. 1-3 , the compression assembly of a single-cylinder compressor may include a main bearing 311, an auxiliary bearing 312, a cylinder 32, a piston 33, and a slide plate 34, and the main bearing 311 is arranged on the axial side of the cylinder 32. At the top, the auxiliary bearing 312 is arranged at the bottom of the cylinder 32 in the axial direction, and a compression chamber 321 is defined between the main bearing 311, the cylinder 32 and the auxiliary bearing 312, and the lower end of the crankshaft 35 passes through the main bearing 311, the cylinder 32 and the auxiliary bearing in sequence 312, the eccentric part 351 of the crankshaft 35 fits in the compression chamber 321, the piston 33 is sleeved on the eccentric part 351 and is located in the compression chamber 321, when the crankshaft 35 rotates, the piston 33 can roll along the inner peripheral wall of the compression chamber 321 .

Referring to Fig. 3, and in combination with Fig. 8-Fig. 13, a sliding vane groove communicating with the compression chamber 321 is formed on the cylinder 32, the sliding vane groove extends along the radial direction of the cylinder 32, and the sliding vane 34 is movably arranged in the sliding vane groove , the rear end of the slide plate 34 can be connected with the slide plate spring, and the slide plate spring pushes the slide plate 34 to move toward the center of the compression chamber 321, so that the tip of the slide plate 34 is always against the outer peripheral wall of the piston 33, thereby The compression chamber 321 can be divided into a suction chamber 3211 and an exhaust chamber 3212 whose volumes change periodically through the cooperation of the sliding plate 34 and the piston 33 .

Referring to Fig. 3, the bottom in the housing 1 has an oil pool, and at least one of the main bearing 311 and the auxiliary bearing 312 is formed with an oil hole 313, that is to say, the main bearing 311 may be formed with an oil hole 313, and the auxiliary bearing 312 An oil hole 313 may also be formed on the main bearing 311 and the auxiliary bearing 312. Both ends of the oil hole 313 communicate with the exhaust chamber 3212 and the oil pool respectively, thus, the oil in the oil pool Lubricating oil can enter the exhaust chamber 3212 through the oil hole 313 .

Specifically, referring to Fig. 7, when the length of the sliding vane 34 extending into the compression chamber 321 is the longest (such as the position reached by the sliding vane 34b shown in Fig. 7, the distance between the piston 33b and the sliding vane groove at this time maximum), that is to say, when the sliding plate 34 moves to the bottom dead center position shown in FIG. Here, it should be noted that the "bottom dead center position" is well known to those skilled in the art, and will not be described in detail here. In addition, the top dead center position refers to the position where the slide plate 34 protrudes into the compression chamber 321 with the smallest length. , such as the position reached by the sliding plate 34a shown in FIG. 7, at this time the distance between the piston 33a and the sliding plate groove is the smallest. In addition, it can be understood that when the rotary compressor 100 is a multi-cylinder compressor, the oil holes 313 may be formed on the partition plate to provide lubricating oil for the tips of the sliding plates 34 in the corresponding compression chambers 321 .

Referring to FIG. 1 , when the rotary compressor 100 is a high back pressure compressor, the suction chamber 3211 and the accumulator 200 can be communicated through the airtight suction pipe assembly 201 (such as the conduit 2011 and the conical pipe 2012 ), thereby accumulating The low-pressure refrigerant in the liquid container 200 can be supplied into the suction chamber 3211 through the airtight suction pipe assembly 201, and the exhaust chamber 3212 communicates with the inside of the shell 1, so that the compressed high-pressure refrigerant can be discharged into the shell through the exhaust chamber 3212. Therefore, the pressure inside the shell 1 is greater than the cavity pressure in the exhaust cavity 3212 before the discharge of refrigerant starts. In this way, when the rotary compressor 100 is working, the cavity pressure difference between the inside of the casing 1 and the exhaust cavity 3212 before the discharge of refrigerant starts to be used, and at the same time, the movement of the sliding plate 34 and the piston 33 is used to control the adjustment nozzle. The size of the opening of the oil hole 313, so as to achieve the purpose of controlling the amount of oil injection and the time of oil injection, realize the oil injection lubrication of the side slide plate 34 and the piston 33 of the exhaust chamber 3212, and improve the contact between the tip of the slide plate 34 and the outer edge of the rolling piston 33 The lubricated state of the contact improves the reliability of the rotary compressor 100 .

In addition, when the rotary compressor 100 is a low-back pressure compressor, the lubricating oil in the oil pool can be introduced into the oil hole 313 according to the accurate flow rate at an appropriate time by setting an oil pump assembly and a regulating device, so as to control the flow of the sliding plate 34. The tip is lubricated, wherein the oil pump assembly and the control device are well known to those skilled in the art. For example, the oil pump assembly may include oil pipes, oil pumps, solenoid valves, etc., and the control device may be a controller.

According to the rotary compressor 100 of the embodiment of the present invention, an oil hole 313 is provided on the supporting member to provide lubricating oil to the tip of the sliding plate 34, thereby improving the lubrication condition of the tip of the sliding plate 34 and reducing the size of the sliding plate. The wear of the tip 34 improves the working reliability of the rotary compressor 100 . In short, the rotary compressor 100 according to the embodiment of the present invention improves the lubrication condition at the tip of the sliding plate 34 by spraying oil through the oil hole 313, so that the rotary compressor 100 has a simple and reasonable structure, high reliability, It has the advantages of long life, low production cost, flexible and convenient operation, and wide application range.

Moreover, when lubricating oil contacts the tip of the sliding plate 34, a stable oil film can be maintained between the outer edge of the piston 33 and the tip of the sliding plate 34, thereby further improving the boundary lubrication state between the sliding plate 34 and the piston 33. In addition, when lubricating oil is sprayed into the exhaust chamber 3212, the temperature of the compression chamber 321 can be reduced, thereby reducing the compression work, increasing the viscosity of the lubricating oil in the compression chamber 321, reducing leakage, and increasing cooling capacity.

Optionally, the oil hole 313 may be a circular hole, an oval hole, an oblong hole or a polygonal hole and the like. That is to say, on a plane perpendicular to the axis of the cylinder 32 , the cross-sectional shape of the oil hole 313 is circular, elliptical, oblong or polygonal. For example, in the example of FIG. 5 , the oil hole 313 may be an oblong hole.

The oil hole 313 extends along the radial direction of the cylinder 32 and is parallel to the moving direction of the sliding plate 34 . For example, in the example of FIG. 7 , the oil hole 313 may be formed as an oblong hole, and on a plane perpendicular to the axis of the cylinder 32 , the length direction of the oil hole 313 is parallel to the moving direction of the sliding plate 34 . Thus, the size of the oil hole 313 can be effectively reduced, the pertinence of the oil injection from the oil hole 313 can be improved, and the lubricating oil ejected from the oil hole 313 can only lubricate the vicinity of the tip of the sliding plate 34, thus avoiding excessive lubricating oil Entering the exhaust chamber 3212 causes the problem of increased oil discharge.

Further, the side wall of the oil hole 313 away from the air suction chamber 3211 is flush with the side wall of the slide plate 34 away from the air suction chamber 3211 . For example, in the examples of Fig. 10 and Fig. 11, the right side wall of the oil hole 313 is flush with the right side wall of the sliding plate 34, so that the size of the oil hole 313 can be further reduced, and the targeted oil injection of the oil hole 313 can be improved. Ensure that the lubricating oil ejected from the oil hole 313 only lubricates the vicinity of the tip of the sliding plate 34, further reducing the amount of oil ejected. Of course, the present invention is not limited thereto, and the side wall of the oil hole 313 away from the air suction cavity 3211 can also be located on the side of the side wall of the sliding plate 34 away from the air suction cavity 3211 adjacent to the air suction cavity 3211, For example, the right side wall of the oil hole 313 shown in FIG. 7 may be located on the left side of the right side wall of the slide plate 34 .

Specifically, referring to Fig. 4 and Fig. 5, the value range of the length L of the oil hole 313 in the direction parallel to the movement direction of the slide plate 34 satisfies: And, 90°≤θ≤270°, where θ is the angle between the line connecting the central axis of the crankshaft 35 and the central axis of the eccentric portion 351 and the centerline of the sliding vane groove, and e is the eccentricity of the crankshaft 35, that is, the crankshaft 35 The length of the line connecting the central axis and the central axis of the eccentric portion 351 , r is the radius of the outer edge of the piston 33 . Here, it should be noted that the length L is a fixed value, and any suitable value within this value range can be selected according to actual requirements to process the oil hole 313 on the support member.

Specifically, referring to FIG. 4 and FIG. 7, the value range of the width D of the oil hole 313 in the direction perpendicular to the movement direction of the slide plate 34 satisfies: Wherein, D _is the thickness of the slide 34 (for example, the thickness of the slide 34a or slide 34b shown in 7 in the left-right direction). For example, in the example of FIG. 7 , when the oil hole 313 is formed as an oblong hole, and the oil hole 313 extends radially of the cylinder 32 and is parallel to the sliding plate 34 , the width D is the diameter of the end of the oil hole 313 . Here, it should be noted that the width D is a fixed value, and any suitable value within this value range can be selected according to actual requirements to process the oil hole 313 on the support member.

Optionally, when the length of the sliding vane 34 protruding into the compression chamber 321 is the longest, the end of the oil hole 313 away from the sliding vane groove is covered by the piston 33 on a horizontal plane perpendicular to the axial direction of the cylinder 32 . For example, in the example of FIG. 10 , when the sliding plate 34 moves to the bottom dead center position, the end of the oil hole 313 away from the sliding plate groove is covered by the piston 33 on the horizontal plane perpendicular to the axial direction of the cylinder 32 .

Or alternatively, when the length of the sliding vane 34 extending into the compression chamber 321 is the longest, on the horizontal plane perpendicular to the axial direction of the cylinder 32, the end of the oil hole 313 away from the sliding vane groove is in contact with the outer peripheral wall of the piston 33 For example, when the oil hole 313 is formed as an oblong hole, and the oil hole 313 extends radially along the cylinder 32 and is parallel to the slide plate 34, the end of the oil hole 313 away from the slide plate groove can be in contact with the outer peripheral wall of the piston 33 cut. Thus, the size of the oil hole 313 can be further reduced, the pertinence of the oil injection from the oil hole 313 can be improved, and the lubricating oil ejected from the oil hole 313 can only lubricate the vicinity of the tip of the sliding plate 34, further reducing the amount of oil ejected.

In one embodiment of the present utility model, the rotary compressor 100 further includes: an oil pipe 314, the oil pipe 314 is arranged on the support with the oil hole 313, and one end of the oil pipe 314 communicates with the oil hole 313, and the other end of the oil pipe 314 Immerse in oil pool. Referring to Fig. 6, an oil hole 313 is formed on the auxiliary bearing 312, and the oil hole 313 can penetrate from the side end surface of the auxiliary bearing 312 adjacent to the cylinder 32 toward a direction away from the cylinder 32, and an oil passage is further formed on the auxiliary bearing 312, One end of the oil passage communicates with the oil hole 313, and the other end of the oil passage runs through the auxiliary bearing 312. One end of the oil pipe 314 can extend from the auxiliary bearing 312 into the oil passage to communicate with the oil hole 313. The other end of the oil pipe 314 is immersed in the oil. The pool is in communication with the lubricating oil, so that the oil pipe 314 can lead the lubricating oil in the oil pool into the oil hole 313 for lubricating the tip of the sliding plate 34 . Therefore, by providing the oil pipe 314 with a simple structure, the structure of the rotary compressor 100 can be effectively simplified, the difficulty of realizing the oil injection effect can be reduced, and the applicability and generalizability of the rotary compressor 100 can be improved. In addition, the oil pipe 314 can throttle the lubricating oil to a certain extent, thereby avoiding the problem of excessive oil injection due to excessive pressure difference.

Specifically, referring to FIG. 1 and FIG. 6 , the angle α between the centerline of the oil pipe 314 and the central axis of the cylinder 32 satisfies: 0≤α<90°. For example, when the included angle α=0° between the centerline of the oil pipe 314 and the central axis of the cylinder 32, the oil pipe 314 can vertically extend into the oil pool, at this time, the length of the oil pipe 314 can be set shorter, To prevent the lower end of the oil pipe 314 from extending into the bottom of the oil pool, and prevent the impurities deposited at the bottom of the oil pool from entering the oil pipe 314 to block the oil pipe 314. When the length of the oil pipe 314 is long, the oil pipe 314 can be arranged so that the center line of the oil pipe 314 is in line with the cylinder. The included angle between the central axes of 32 is 0°<α<90°, for example, the included angle between the central axis of oil pipe 314 and the central axis of cylinder 32 can be 10°, 20°, 30°, 40°, 50° , 60°, 70° or 80°, etc., so as to further prevent the lower end of the oil pipe 314 from extending into the bottom of the oil pool, and prevent the impurities at the bottom of the oil pool from entering the oil pipe 314.

Specifically, referring to FIG. 1 , the cylinder 32 has a suction hole communicating with the suction chamber 3211, and one end of the suction pipe assembly 201 for introducing the refrigerant in the accumulator 200 into the suction chamber 3211 as described above can be Extending into and fitting in the suction hole, the other end of the oil pipe 314 is opposite to the central axis of the suction hole in the axial direction of the cylinder 32, that is to say, the suction end of the oil pipe 314 can be located directly below the central axis of the suction hole , so that the oil pipe 314 can suck the lubricating oil directly below the suction hole. In this way, during the operation of the rotary compressor 100, the lubricating oil near the suction hole is cooled by the suction refrigerant and the temperature is relatively low. After the suction end of the oil pipe 314 is inserted into the oil pool directly below the suction hole, the oil pipe 314 Lubricating oil with a relatively low temperature in this area can be extracted to spray into the exhaust cavity 3212, so that the exhaust cavity 3212 can be better cooled, compression loss, compression process work, leakage, and cooling capacity can be reduced. At the same time, due to the temperature Lower oils have a higher viscosity for better lubrication and sealing. To a certain extent, it improves the lubricating, cooling and sealing functions of lubricating oil.

Next, the working process of the rotary compressor 100 according to one embodiment of the present invention will be briefly described with reference to FIGS. In the process, through the reciprocating motion of the sliding plate 34 and the rolling of the piston 33, the regular opening and closing of the oil injection hole 313 is realized to lubricate the tip of the sliding plate 34, wherein the size of the oil injection hole 313 affects the injection A key factor in oil quantity and injection timing.

As shown in Figures 8 and 9, when the piston 33 moves to a position before the bottom dead center position, there is a large gap between the high-pressure side at the tip of the slide plate 34 and the outer edge of the piston 33, so that the oil injection hole 313 is exposed. At this time, the fuel injection can start. Since the pressure in the exhaust chamber 3212 is small at this time, the pressure difference with the inside of the housing 1 is relatively large, and the area of the exposed fuel injection hole 313 is large, and the fuel injection volume at this time is large.

As shown in Figures 10 and 11, when the piston 33 moves to the bottom dead center position, the gap formed between the tip of the sliding plate 34 and the outer edge of the piston 33 decreases, and the pressure in the exhaust chamber 3212 increases, and the internal and external pressure difference decreases. Small, the fuel injection volume is reduced.

As shown in Figures 12 and 13, when the piston 33 moves to a position after the bottom dead center, the pressure in the exhaust chamber 3212 is close to the exhaust pressure inside the housing 1, and as the slide plate 34 and the piston 33 move up , the gap formed by the two gradually decreases until it disappears, and finally the oil injection hole 313 will be covered by the piston 33, and the oil injection stops.

When the rotary compressor 100 is in operation, the above-mentioned oil injection state is always cycled, and the reciprocating motion of the sliding vane 34 and the rolling of the piston 33 periodically open and close the oil injection hole 313, thereby achieving targeted lubrication of the tip of the sliding vane 34, and at the same time The oil injection quantity and oil injection time are well controlled to ensure reliable performance of the rotary compressor 100 .

In short, in the high back pressure compressor, the pressure inside the shell 1 is the discharge pressure, so the pressure above the oil pool is also at the discharge pressure, between the start point of the compression stroke and the start point of the discharge stroke, The closed volume defined by the cylinder 32, the piston 33 and the sliding plate 34 changes from the suction pressure to the exhaust pressure, so that the lubricating oil in the oil pool can be introduced into the exhaust chamber 314 by setting the oil hole 313 and the oil pipe 313, so as to improve the pressure of the piston. 33 and the sliding plate 34, and the sliding plate 34 and the piston 33 jointly control the opening and closing of the oil hole 313 during the oil injection process, that is, when the oil hole 313 is open, the lubricating oil is allowed to be sprayed into the cylinder 32, and when the compression The rest of the stroke prevents the injection of oil.

To sum up, according to the rotary compressor 100 of the embodiment of the present utility model, the oil hole 313 under the moving track of the sliding vane 34 is opened on the support member close to the high-pressure side of the sliding vane 34 , through the connection between the sliding vane 34 and the piston 33 Coordinated movement and cooperative work can effectively spray oil to lubricate the front end of the sliding plate 34. The amount of oil sprayed will effectively decrease with the increase of the rotation angle, so as to avoid excessive lubricating oil entering the compression chamber 321 and increasing the spit. Oil problem.

Because the temperature of the suction chamber 3211 is relatively low and the temperature of the exhaust chamber 3212 is relatively high, the temperature field distribution around the circumferential direction of the cylinder 32 is not uniform. The lubricating oil is introduced into the oil hole 313 and sprayed into the exhaust chamber 3212, which can improve the lubricating, cooling and sealing effects of the lubricating oil to a certain extent, improve the reliability of the sliding plate 34, reduce the work of the compression process, reduce leakage, and improve Cooling capacity.

In describing the present invention, it should be understood that the terms "center", "length", "width", "thickness", "upper", "lower", "left", "right", "vertical" , "horizontal", "top", "bottom", "inner", "outer", "axial", "radial", "circumferential", etc. indicate the orientation or positional relationship based on the orientation shown in the drawings or positional relationship, are only for the convenience of describing the utility model and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation, and therefore cannot be construed as a limitation of the utility model .

In this utility model, unless otherwise specified and limited, terms such as "installation", "connection", "connection" and "fixation" should be understood in a broad sense, for example, it can be a fixed connection or a detachable connection. Connected, or integrated; it can be directly connected or indirectly connected through an intermediary, and it can be the internal communication of two elements or the interaction relationship between two elements. Those of ordinary skill in the art can understand the specific meanings of the above terms in the present utility model according to specific situations.

In the description of this specification, descriptions referring to the terms "one embodiment", "some embodiments", "example", "specific examples", or "some examples" mean that specific features described in connection with the embodiment or example , structures, materials or features are included in at least one embodiment or example of the present invention. In this specification, the schematic representations of the above terms are not necessarily directed to the same embodiment or example. Furthermore, the described specific features, structures, materials or characteristics may be combined in any suitable manner in any one or more embodiments or examples. In addition, those skilled in the art can combine and combine different embodiments or examples and features of different embodiments or examples described in this specification without conflicting with each other.

Although the embodiments of the present invention have been shown and described, those skilled in the art can understand that various changes, modifications, substitutions and modifications, the scope of the present invention is defined by the claims and their equivalents.

Claims (12)

1. A rotary compressor, characterized in that, comprising: a housing having an oil sump therein; and a compression mechanism, the compression mechanism includes two bearings, a cylinder, a piston, a sliding plate and a crankshaft, the two bearings are arranged at both axial ends of the cylinder to define a compression chamber with the cylinder, The lower end of the crankshaft passes through the two supports and the cylinder, the piston is sleeved on the crankshaft and is located in the compression chamber, and a slide communicating with the compression chamber is formed on the cylinder. The sliding piece is movably arranged in the sliding piece groove, and the tip of the sliding piece abuts against the outer peripheral wall of the piston to separate the compression chamber into a suction chamber and an exhaust chamber , at least one of the two supporting members is formed with an oil hole, and the lubricating oil in the oil pool is suitable for entering the exhaust chamber through the oil hole to lubricate the tip of the sliding plate, Wherein, when the length of the sliding piece extending into the compression chamber is the longest, the tip of the sliding piece covers at least part of the oil hole. 2. The rotary compressor according to claim 1, wherein when the length of the sliding vane protruding into the compression chamber is the longest, on a horizontal plane perpendicular to the axial direction of the cylinder, the An end of the oil hole away from the sliding vane groove is in contact with the outer peripheral wall of the piston or is covered by the piston. 3. The rotary compressor according to claim 1, wherein the oil hole extends radially of the cylinder and is parallel to the sliding plate. 4. The rotary compressor according to claim 3, characterized in that, the side wall of the oil hole away from the suction chamber is connected to the side wall of the sliding vane far away from the suction chamber. The walls are flush. 5. The rotary compressor according to claim 1, characterized in that, the length L of the oil hole parallel to the moving direction of the sliding vane satisfies: Wherein, 90°≤θ≤270°, wherein, e is the eccentricity of the crankshaft, and r is the radius of the outer edge of the piston. 6. The rotary compressor according to claim 1, characterized in that, the width D of the oil hole perpendicular to the moving direction of the sliding vane satisfies: Wherein, D _is the thickness of the slide. 7. The rotary compressor according to claim 1, further comprising: An oil pipe, the oil pipe is arranged on the at least one of the two support members, and one end of the oil pipe communicates with the oil hole, and the other end of the oil pipe is immersed in the oil pool. 8 . The rotary compressor according to claim 7 , wherein the angle α between the centerline of the oil pipe and the central axis of the cylinder satisfies: 0≤α<90°. 9. The rotary compressor according to claim 7, wherein the cylinder has a suction hole communicating with the suction chamber, wherein the other end of the oil pipe is connected to the suction hole. The central axes are opposite in the axial direction of the cylinders. 10. The rotary compressor according to any one of claims 1-9, characterized in that, the oil hole is a circular hole, an oval hole, an oblong hole or a polygonal hole. 11. The compressor according to claim 1, characterized in that there is one cylinder, and the two supporting members are a main bearing and an auxiliary bearing. 12. The compressor according to claim 1, characterized in that there are multiple cylinders, a partition is provided between every two adjacent cylinders, and at least one of the two supporting members For the separator.