JPH04330395A - Rolling piston type compressor - Google Patents

Abstract

PURPOSE:To improve volume efficiency through prevention of leakage of fluid by preventing production of a small gap between the outer peripheral surface and the inner peripheral surface of a cylinder. CONSTITUTION:An oil feed passage 14a having the one end opened to a main oil feed passage 13 and the other end opened to the outer peripheral surface, positioned in an eccentric direction, of a cam part 3e is formed in the cam part 3e of a drive shaft 3b. A roller 6 is pressed against a cylinder 5 by means of an oil pressure of lubricating oil 0 flowing through the oil feed passage 14a and no gap between the outer peripheral surface of the roller 6 and the inner peripheral surface of the cylinder 5 is produced.

Description

[Detailed description of the invention]

0001

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a rolling piston compressor, and more particularly to measures to prevent fluid leakage between a roller and a cylinder.

0002

2. Description of the Related Art In general, a rolling piston type compressor as disclosed in Japanese Patent Application Laid-Open No. 167095/1983 is known as one type of compressor installed in refrigerators and the like. This type of compressor includes an electric motor and a compressor main body connected to the electric motor via a crankshaft housed in a casing. In the compressor main body, a roller as a rolling piston is disposed in the cylinder, and this roller is disposed eccentrically with respect to the cylinder, and its outer peripheral surface A part of the cylinder comes into contact with the inner circumferential surface of the cylinder. Further, a front head and a rear head are attached to each of the upper and lower end surfaces of the cylinder, and a compression chamber is formed between the inner peripheral surface of the cylinder and the outer peripheral surface of the roller. Further, the cylinder is provided with a blade whose tip abuts against the outer peripheral surface of the roller so as to be able to move in and out of the compression chamber. On the other hand, a cam portion of a crankshaft extending from the electric motor is fitted into the roller. Furthermore, the case
Lubricating oil is stored at the bottom of the thing, and the lower end of the crankshaft is immersed in this lubricating oil. Further, this lubricating oil is supplied to each sliding portion by an oil pump provided at the lower end of the crankshaft.

When this compressor is driven, the volume of the compression chamber is changed by the rotation of the rollers in conjunction with the rotation of the crankshaft, thereby causing fluid such as refrigerant to flow into the cylinder. It is designed to be compressed.

0004

[Problems to be Solved by the Invention] In the rolling piston type compressor as described above, as the roller rotates, the lubricating oil that is present between the roller and the cylinder decreases. An oil film reaction force is generated, and this oil film reaction force acts on the roller in a direction away from the cylinder, creating a small gap between the outer peripheral surface of the roller and the inner peripheral surface of the cylinder. There is. If such a small gap occurs, the high-pressure chamber and low-pressure chamber of the compression chamber will communicate, causing high-pressure fluid in the high-pressure chamber to leak into the low-pressure chamber, reducing the volumetric efficiency of the compressor. There was a problem.

The present invention has been made in view of this point, and it is an object of the present invention to prevent a gap from forming between the outer circumferential surface of the roller and the inner circumferential surface of the cylinder.

[0006]

[Means for Solving the Problems] In order to achieve the above object, the present invention utilizes the pressure of lubricating oil to press the roller toward the cylinder side. Specifically, the invention according to claim 1 provides a driving means (3) and a compression means (4) connected to the driving means (3) in a casing (2) in which lubricating oil (O) is stored. ) is accommodated, and the compression means (4) has a roller (6) eccentrically housed in the cylinder (5) so that a part of the outer circumferential surface of the roller (6) overlaps with the inner circumferential surface of the cylinder (5). An eccentric portion (3e) formed eccentrically in a predetermined direction from the axis of the drive shaft (3b) of the drive means (3) is inserted into the roller (6). A main oil supply passage (13) is formed through the drive shaft (3b). Further, head portions (7) and (8) are arranged and formed on both end surfaces of the cylinder (5) to compress the air between the inner circumferential surface of the cylinder (5) and the outer circumferential surface of the roller (6). A chamber (9) is formed, a fluid suction path (5a) and a fluid discharge path (5d) are connected to the compression chamber (9), and the driving means (3)
) is driven, the roller (6) rotates within the cylinder (5), sucks fluid into the compression chamber (9) from the suction path (5a), and compresses the fluid. A rolling piston type compressor is assumed. The eccentric portion (3e) of the drive shaft (3b) is provided with a hydraulic pressure having one end opened to the main oil supply path (13) and the other end opened to an outer circumferential surface located in the eccentric direction of the eccentric portion (3e). Supply path (14a
).

The invention according to claim 2 has the same premise as the invention according to claim 1, and the eccentric portion (3e) of the drive shaft (3b)
is provided with a hydraulic pressure supply passage (14a) whose one end opens to the main oil supply passage (13) and whose other end opens to the outer peripheral surface located in the eccentric direction of the eccentric part (3e).
) is provided with a low-pressure passage (16) that opens on the outer circumferential surface located in the opposite direction to the eccentric direction of the suction passage (5a) and has the other end open to the suction passage (5a).

[0008] The invention according to claim 3 is based on claim 1 or 2.
In the rolling piston type compressor described, one end opens to the main oil supply passage (13) and the other end opens to the hydraulic supply passage (14).
a) An oil supply passage (14b) is provided that opens on the front side in the rotational direction of the roller (6) than the other end opening, and the other end opening of the oil supply passage (14b) is connected between the roller (6) and the cylinder ( 5) is configured to be set at a position where the oil film reaction force of the lubricating oil (O) interposed between the lubricating oil (O) and the lubricating oil (O) acts.

According to a fourth aspect of the invention, in the rolling piston compressor according to the third aspect, an oil supply passage (14b) is connected to an outer circumferential surface of the eccentric portion (3e), and at least:
The roller (6) is connected to the other end opening of the hydraulic supply path (14a).
Oil supply grooves (15
).

[0010] The invention described in claim 5 is based on claims 1, 2, and 3.
Or in the rolling piston type compressor described in 4,
An eccentric part (
3e) with a flat notch across both end faces of the roller (6).
Hydraulic working space (A) between the inner peripheral surface and the eccentric part (3e)
The structure was designed to form a

[0011] The invention described in claim 6 is based on claims 1, 2, and 3.
In the rolling piston compressor described in , 4 or 5, the end face of the eccentric part (3e) is set at a position with a predetermined dimension from the head parts (7), (8).

0012

[Function] With the above structure, the present invention provides the following functions. In the invention according to claim 1, as the drive means (3) is driven, the roller (6) of the compression means (4)
) rotates within the cylinder (5), thereby opening the suction passage (
5a) into the compression chamber (9) to compress the fluid. After that, this compressed fluid flows through the discharge path (5d)
It is discharged from the inside space of the casing (2). Simultaneously with this operation, the lubricating oil (O) stored in the casing (2) passes through the main oil supply path (13) and is supplied to each sliding portion to lubricate them. A part of the lubricating oil (O) passing through the main oil supply path (13) is introduced into the oil pressure supply path (14a), and the oil pressure causes the roller (6
) toward the cylinder (5). by this,
There is no gap between the outer circumferential surface of the roller (6) and the inner circumferential surface of the cylinder (5), thus preventing fluid from leaking from the high pressure chamber (9b) to the low pressure chamber (9a). This improves volumetric efficiency.

[0013] In the invention according to claim 2, in addition to the effect in the invention according to claim 1 described above, the low pressure passage (16)
Low pressure is introduced to the side, and the pressure difference between the opening at the other end of the hydraulic supply passage (14a) and the opening at the low pressure passage (16) in the eccentric portion (3e) becomes large. )
A large pressing force on the cylinder (5) can be obtained. Therefore, leakage of fluid between the roller (6) and the cylinder (5) can be more reliably prevented.

[0014] In the invention according to claim 3, the oil supply path (14b
) The oil pressure of the lubricating oil (O) flowing through the inner circumferential surface of the cylinder (5) is proportional to the oil film reaction force of the lubricating oil (O) interposed between the outer circumferential surface of the roller (6) and the inner circumferential surface of the cylinder (5). As a result, the oil film reaction force, which was the cause of the gap between the roller (6) and the cylinder (5), is attenuated, thereby further preventing fluid leakage. It can definitely be prevented.

[0015] In the invention according to claim 4, the oil supply path (14b
) is introduced into the oil supply groove (15) to lubricate between the eccentric portion (3e) and the roller (6). Therefore, mechanical losses of the compressor are reduced and compressor efficiency is improved.

In the invention set forth in claim 5, the hydraulic space (A) is formed between the inner circumferential surface of the roller (6) and the eccentric portion (3e), so that the roller (6) ) can increase the area of action of the hydraulic pressure acting on the roller (6).
A large pressing force on the cylinder (5) can be ensured.

[0017] In the invention according to claim 6, the eccentric portion (3e)
By making the end face of the head part (7), (8) have a predetermined dimension, mechanical loss due to sliding between the eccentric part (3e) and the head parts (7), (8) is eliminated. Not only the compressor efficiency is improved, but also this eccentric part (
The space formed between the head parts (7) and (8) has an intermediate pressure, and the pressure difference between the pressure inside the compression chamber (9) and the pressure inside the compression chamber (9) can be reduced. Fluid leakage from the end face is suppressed.

[0018]

【Example】

(First Embodiment) Next, a first embodiment of the present invention will be described with reference to the drawings. As shown in FIG. 3, the rolling piston compressor (1) according to the present invention has a casing (2)
There is a drive means (3) and a compressor main body (4) as a compression means inside.
).

The drive means (3) consists of an electric motor (3a) and a crankshaft (3b) as a drive shaft. The electric motor (3a) operates in the internal space (
a stator (3c) disposed on the upper part of the casing (2a) and fixed to the inner circumferential surface of the casing (2);
The rotor (3d) is arranged at the center of the rotor. The crankshaft (3b) has an upper end connected to the center of the rotor (3d), and a lower end extending downward and connected to the compressor main body (4). In addition, lubricating oil (O
) is stored, and the lower end of the crankshaft (3b) is immersed in this lubricating oil (O). A centrifugal pump (3f) is disposed at the lower end of this crankshaft (3b), and a main oil supply passage (13) (see Fig. 1) extending vertically passes through the crankshaft (3b). When the compressor (1) is driven, the centrifugal pump (3
f), the lubricating oil (O) is pumped up into the main oil supply path (13) and then supplied to each sliding portion of the compressor (1).

[0020] The compressor main body (4) has a fixed airfoil shape,
It is arranged below the electric motor (3a). As shown in FIGS. 3 and 4, this compressor main body (4) has a roller (6) housed in a cylinder (5) fixed to the inner wall of the casing (2). At the same time, a front head (
7) has a rear head (also a head part) on the lower end surface.
8) are attached respectively, and this front head (7
) and the rear head (8), a compression chamber (9) is formed between the inner peripheral surface of the cylinder (5) and the outer peripheral surface of the roller (6). The cylinder (5) also has a compression chamber (
A refrigerant suction passage (5a) opening to the refrigerant refrigerant 9) is formed, and a suction pipe (10) extending from an accumulator (not shown) is connected to the suction passage (5a). On the other hand, in the center of the roller (6), a cam portion is formed integrally with the crankshaft (3b) and is eccentric in a predetermined direction with respect to the axis of the crankshaft (3b). (3e) is inserted. As a result, the roller (6) is provided eccentrically with respect to the cylinder (5), and a portion of the outer peripheral surface of the roller (6) comes into contact with the inner peripheral surface of the cylinder (5). ing. Additionally, a slight clearance is provided between the inner circumferential surface of the roller (6) and the outer circumferential surface of the cam portion (3e). Relative rotational movement can be performed smoothly. Further, the height of the cam portion (3e) matches the height of the cylinder (5), and the upper and lower end surfaces of the cam portion (3e) are connected to the front and rear heads (7) and (8). They are in contact with each other. Further, a blade groove (5b) is formed in the vicinity of the position where the suction passage (5a) is arranged in the cylinder (5). The blade groove (5b) is connected to the cylinder (5b).
), it extends in the radial direction of the cylinder (5), penetrates both the upper and lower end surfaces of the cylinder (5), and its outer peripheral side is connected to the outer peripheral wall (5c
) is closed. Further, a blade (11) is disposed in the blade groove (5b) so as to be freely retractable into the cylinder (5). The tip of the blade (11) is pressed against the roller (6) by the biasing force of a spring (11a) disposed between the rear end surface and the outer circumferential wall (5c) of the cylinder (5). ) is pressed against the outer peripheral surface of the compression chamber (9
) is divided into a low pressure chamber (9a) and a high pressure chamber (9b). Furthermore, a discharge passage (5d) is provided on the high pressure chamber (9b) side near the location where the blade (11) is disposed. This discharge passage (5d) has one end opened at the inner circumferential surface of the cylinder (5), and a lead (not shown) that can be opened as the pressure inside the high pressure chamber (9b) increases. A valve is provided. On the other hand, the other end of this discharge passage (5d) is opened into the internal space (2a) of the casing (2). Further, through holes (7a), (8a) are formed in the front and rear heads (7), (8) and have a diameter slightly larger than that of the crankshaft (3b) and extend in the vertical direction. The crankshaft (3) is inserted into the through holes (7a) and (8a).
b) is rotatably supported via a metal seal. On the other hand, a discharge pipe (12) leading to a condenser (not shown) is connected to the upper surface of the casing (2), and the high temperature and high pressure refrigerant discharged from the compressor main body (4) is carried out through this discharge pipe 12) to the condenser side. With this configuration, when driving the compressor, the electric motor
As the crankshaft (3b) is rotated by the drive of the cylinder (3a), the roller (6) rotates within the cylinder (5) and contracts the compression chambers (9a) and (9b). It has become.

Next, the features of the present invention will be explained. As shown in FIGS. 1 and 2, the cam portion (3e
), a sub-oil supply passage (14) is formed that branches from the main oil supply passage (13) and extends in the radial direction of the crankshaft (3b), that is, in the horizontal direction. This sub-oil supply path (14) consists of a first oil supply path (14a) as a hydraulic pressure supply path in the present invention and a second oil supply path (14b) as an oil supply path. The first oil supply passage (14a) has one end open to the main oil supply passage (13), and extends horizontally from this opening toward the eccentric direction of the cam portion (3e) with respect to the crank axis (see FIGS. 1 and 2). After extending in the right direction), the other end opens at the outer surface of the cam portion (3e). In other words, this other end opening position is the roller (6)
is set so as to face the position where the outer circumferential surface of the cylinder (5) abuts on the inner circumferential surface of the cylinder (5), and this first oil supply path (14a
) is configured so that the oil pressure of the lubricating oil (O) flowing through the roller (6) is applied to the inner peripheral surface of the roller (6). Further, the opening area of the other end opening is formed to have a slightly larger diameter than the passage area of the first oil supply path (14a), so that hydraulic pressure can be applied over a wide range. 2nd oil supply path (1
4b) has one end open to the main oil supply passage (13), and a predetermined path from this opening to the front side in the rotational direction of the roller (6) with respect to the opening position of the other end of the first oil supply passage (14a). extending in the radial direction of the crankshaft (3b) at an angle,
The other end is open to the outer surface of the cam portion (3e). The opening portion is formed to have a slightly larger diameter similarly to the first oil supply passage (14a). Also, as shown in Figure 5,
This second oil supply path (14b) is provided on the outer peripheral surface of the cam portion (3e).
) from the edge of the other end opening in the rotation direction of the roller (6), that is, a position facing the other end opening of the first oil supply path (14a) in the diametrical direction of the roller (6) A spiral groove (15) is formed as a shallow groove-shaped oil supply groove, and this spiral groove (15) allows the lubricating oil (O) flowing through the second oil supply passage (14b) to be transferred to the second oil supply passage (14b). The other end of the first oil supply passage (14a) is guided to the opposite side from the opening position.

Next, this rolling piston compressor (
1) during operation will be explained. First, the electric motor (3
When a) is driven, this driving force is transmitted to the roller (6) of the compressor body (4) via the crankshaft (3b), and the roller (6) rotates within the cylinder (5). do. As a result, refrigerant gas flows from the suction pipe (10) through the suction path (5a) into the low pressure chamber (9a) of the compressor main body (4). Thereafter, as the roller (6) rotates, the low pressure chamber (9a) becomes the high pressure chamber (9b), compressing the refrigerant gas, and when the pressure of this refrigerant gas reaches a predetermined value, this pressure The reed valve opens, and high-pressure refrigerant gas flows through the discharge path (5d
) into the internal space (2a) of the casing (2),
Thereafter, it is led out to the condenser side through the discharge pipe (12). In addition, under such operating conditions, the casing (2
) has a high pressure atmosphere.

As the crankshaft (3b) rotates, the centrifugal pump (3f) opens the main oil supply path (1).
The lubricating oil (O) pumped up in 3) is supplied to each sliding part in the compressor (1) to lubricate each part. To explain the characteristic effect of this example, a part of the lubricating oil (O) flowing in this main oil supply passage (13) is guided to the sub oil supply passage (14), and this sub oil supply passage (14) The lubricating oil (O) led to the first oil supply path (14a) flows from the other end opening of this first oil supply path (14a) toward the inner circumferential surface of the roller (6). Hydraulic pressure acts to push the roller (6) toward the cylinder (5) (toward the right in FIGS. 1 and 2). In this way, the roller (6) is pressed against the cylinder (5), and when this pressure overcomes the oil film reaction force shown by the arrow in FIG. 2, the roller (6) and the cam part (3e) The roller (
6) moves toward the cylinder (5). For this purpose,
There will no longer be a small gap at the contact area between the cylinder (6) and the cylinder (5), and therefore no leakage of refrigerant gas from the high pressure chamber (9b) to the low pressure chamber (9a) will occur. , the volumetric efficiency of the compressor (1) is improved. On the other hand, the oil pressure caused by the lubricating oil (O) guided to the second oil supply path (14b) acts in a direction substantially opposite to the direction of action of the oil film reaction force shown by the arrow in FIG. The oil film reaction force is attenuated, and refrigerant leakage between the above-mentioned roller (6) and cylinder (5) is more reliably prevented. Further, a part of the lubricating oil (O) that has passed through the second oil supply path (14b) is supplied toward the opposite side of the other end opening of the first oil supply path (14a) through the spiral groove (15). , the roller (6) is moved by the movement of the roller (6).
This is intended to lubricate the area where the distance between the cam part (3e) and the cam part (3e) is narrow, that is, the periphery of the outer peripheral surface of the cam part (3e) in the direction opposite to the eccentric direction.

As described above, according to the configuration of this example, the roller (6) and the cylinder (5) are moved by using the oil pressure of the lubricating oil (O).
By increasing the contact pressure with the high pressure chamber (9b
) to the low pressure chamber (9a) can be prevented, and the volumetric efficiency of the compressor (1) can be significantly improved.

Hereinafter, a modification of the first embodiment will be explained. What is shown in FIG. 6 shows a modification of the opening at the other end of the first oil supply passage (14a), in which the crankshaft (3b)
By cutting out the cam part (3e) in a planar shape from the upper end to the lower end, a hydraulic pressure having a crescent shape in plan view is formed between the inner circumferential surface of the roller (6) and the eccentric part (3e). Action space (A
), thereby increasing the pressure acting area of the opening at the other end of the first oil supply passage (14a). With such a configuration, this first oil supply path (1
4a) The pressure-receiving area of the inner circumferential surface of the roller (6) that receives the hydraulic pressure of the lubricating oil (O) flowing through the roller (6) increases, and the roller (6)
A large pressing force against the cylinder (5) can be ensured, and refrigerant leakage from the high pressure chamber (9b) to the low pressure chamber (9a) can be prevented even more reliably.

FIG. 7 shows another modification in which the height dimension of the cam portion (3e) is changed between the cylinder (5) and the roller (
6), and small gaps are formed between the upper and lower end surfaces and the front and rear heads (7) and (8). According to such a configuration, each end face of the cam part (3e) and each head (7), (8)
Since these parts do not slide, there is no friction loss in this part, and the mechanical efficiency of the compressor as a whole is improved. In addition, each end face of this cam part (3e) and each head (7),
(8) The space formed between the low pressure chamber (9a)
Since the pressure is approximately intermediate between the pressures in the space and the compression chamber (9b), refrigerant leaks from each end face of the roller (6) between this space and the compression chamber (9). is suppressed, thereby also improving volumetric efficiency.

(Second Embodiment) Next, a second embodiment of the present invention will be described. In this example, members similar to those in the first example described above are given the same reference numerals, and only the characteristic features of this example will be described. As shown in FIG. 8, the compressor (1) of this example is provided with a low pressure passage (16). This low pressure passage (16) has one end with a cam portion (3
e) is opened on the outer peripheral surface opposite to the other end opening of the first oil supply path (14a), that is, in the opposite direction to the eccentric direction of the cam portion (3e). This low pressure passage (16) is connected from this opening to the cam portion (3e).
After being extended in the axial direction with a small dimension, it is bent upward and the crankshaft (
3b) is bent radially outward. After extending in the radial direction inside the front head (7), the cylinder (
5) is bent downward at the upper position, extends downward within this cylinder (5), and the other end is connected to the suction passage (5a).
) is open. Furthermore, a ring-shaped groove (7b) is formed in the inner wall of the front head (7), so that both openings of this low pressure passage (16) are always communicated even when the crankshaft (3b) rotates. It has become. By forming such a low pressure passage (16), the cam portion (
The outer peripheral surface of 3e) and the suction passage (5a) are communicated with each other. Therefore, the first oil supply path (14) of this cam portion (3e)
The low pressure of the suction path (5a) is introduced into the portion opposite to the other end opening of a).

[0028] The compressor (1
), on the first oil supply path (14a) side, the roller (6) is pressed toward the cylinder (5) by the hydraulic pressure of the lubricating oil (O) in the same manner as in the first embodiment described above. ing. At the same time, on the low pressure passage (16) side, since the low pressure of the suction passage (5a) is introduced, the roller (6
) and the cam part (3e), the low pressure passage (
16) The pressure distribution state is such that the pressure gradually decreases toward the opening position. Therefore, the pressure difference between the right side and the left side of the cam part (3e) in FIGS. 8 and 9 becomes large, and as a result, the pressure that presses the roller (6) against the cylinder (5) becomes even larger. Refrigerant leakage between the cylinder (6) and the cylinder (5) can be more reliably prevented. In addition, in this example, the first oil supply path (14a)
The lubricating oil (O) supplied into the roller (6) from the roller (6) passes through the outer peripheral surface of the roller (6) and is guided to the low pressure passage (16). (6) and the cam part (
3e), lubrication is achieved over the entire circumference, and the spiral groove as shown in the first embodiment described above is not required.

Although the present embodiment has been described with respect to a compressor installed in an air conditioner, the present invention is not limited to this, but can be applied to various fluid compressors.

[0030]

[Effects of the Invention] As described above, according to the present invention, the following effects are achieved. According to the invention described in claim 1, the roller is pressed toward the cylinder by the hydraulic pressure of the lubricating oil introduced into the hydraulic pressure supply path, and a gap is created between the outer circumferential surface of the roller and the inner circumferential surface of the cylinder. This prevents fluid from leaking from the high pressure chamber to the low pressure chamber.
It is possible to improve the volumetric efficiency of the compressor.

According to the second aspect of the invention, the low pressure passage side communicating with the suction passage is provided to increase the pressure difference between the opening at the other end of the hydraulic pressure supply passage and the opening of the low pressure passage in the eccentric portion. Therefore, a large pressing force of the rollers against the cylinder can be obtained, and leakage of fluid between the rollers and the cylinder can be more reliably prevented.

According to the third aspect of the invention, the oil supply path is provided so that the oil supply path is provided so that the oil supply path flows in a direction substantially opposite to the oil film reaction force of the lubricating oil interposed between the outer peripheral surface of the roller and the inner peripheral surface of the cylinder. Since the hydraulic pressure is applied to attenuate the oil film reaction force which is the cause of the gap between the roller and the cylinder, leakage of fluid can be more reliably prevented.

According to the fourth aspect of the invention, part of the lubricating oil flowing through the oil supply path is introduced into the oil supply groove to lubricate between the eccentric portion and the roller over the entire circumference thereof. Therefore, the mechanical loss of the compressor is reduced and the compressor efficiency can be improved.

According to the fifth aspect of the invention, a hydraulic pressure space is formed between the inner circumferential surface of the roller and the eccentric portion, so that the surface area of the hydraulic pressure acting on the roller is increased. Therefore, it is possible to ensure a large pressing force of the roller against the cylinder, and this also makes it possible to improve the fluid leakage prevention function.

According to the invention as set forth in claim 6, the end face of the eccentric portion has a predetermined size with respect to the head portion so that the eccentric portion and the head portion do not slide.
Not only does this eliminate mechanical loss in this part, improving compressor efficiency, but since the space formed between this eccentric part and the head part becomes an intermediate pressure, the pressure difference between the pressure inside the compression chamber and the pressure inside the compression chamber increases. can be made small, and leakage of fluid from the roller end face is suppressed, thereby also improving volumetric efficiency.

[Brief explanation of drawings]

FIG. 1 is a vertical cross-sectional view of the vicinity of a compressor main body in a first embodiment.

FIG. 2 is a cross-sectional view at a position corresponding to line II-II in FIG. 1;

FIG. 3 is a longitudinal sectional view of the compressor.

FIG. 4 is a cross-sectional view of the compressor main body.

FIG. 5 is a perspective view of the vicinity of the cam portion of the crankshaft.

FIG. 6 is a diagram corresponding to FIG. 2 in a modified example.

FIG. 7 is a diagram corresponding to FIG. 1 in another modification.

FIG. 8 is a diagram corresponding to FIG. 1 in a second embodiment.

FIG. 9 is a diagram corresponding to FIG. 2 in a second embodiment.

FIG. 10 is a diagram corresponding to FIG. 5 in the second embodiment.

[Explanation of symbols]

(1) Rolling piston compressor (2)
Casing (3) Drive means (3b) Crankshaft (drive shaft) (3e)
Cam part (eccentric part) (4) Compressor body (compression means) (5)
Cylinder (5a) Suction passage (5d) Discharge passage (6) Roller (7) Front head (head part) (8)
Rear head (head part) (9)
Compression chamber (13) Main oil supply path (14a) First oil supply path (hydraulic supply path) (14b)
2nd oil supply path (oil supply path) (15) Spiral groove (oil supply groove) (16)
Low pressure passage (O) Lubricating oil (A) Hydraulic working space

Claims (6)

[Claims] 1. A driving means (3) and a compression means (4) connected to the driving means (3) are housed in a casing (2) in which lubricating oil (O) is stored, and the compressing means (4) is connected to the driving means (3). Compression means (4
) is a cylinder (5) in which a roller (6) is housed eccentrically so that a part of the outer circumferential surface of the roller (6) comes into contact with the inner circumferential surface of the cylinder (5). - An eccentric part (3e) formed eccentrically in a predetermined direction from the axis of the drive shaft (3b) of the drive means (3) is inserted into the roller (6), and the drive shaft (3b) is provided with main oil supply. A passage (13) is formed through the cylinder (5), and a head portion (7) is formed on both end surfaces of the cylinder (5).
), (8) are arranged and formed to form a compression chamber (9) between the inner peripheral surface of the cylinder (5) and the outer peripheral surface of the roller (6). is connected to a fluid suction passage (5a) and a fluid discharge passage (5d), and as the driving means (3) is driven, the roller (6) rotates within the cylinder (5), and the In a rolling piston type compressor configured to suck fluid into a compression chamber (9) from a suction passage (5a) and compress the fluid, an eccentric portion (3e) of the drive shaft (3b) is characterized in that a hydraulic pressure supply path (14a) is provided, one end of which opens to the main oil supply path (13), and the other end of which opens to the outer peripheral surface located in the eccentric direction of the eccentric portion (3e). A rolling piston type compressor. 2. A driving means (3) and a compression means (4) connected to the driving means (3) are housed in a casing (2) in which lubricating oil (O) is stored, and the compressing means (4) is connected to the driving means (3). Compression means (4
) is a cylinder (5) in which a roller (6) is housed eccentrically so that a part of the outer circumferential surface of the roller (6) comes into contact with the inner circumferential surface of the cylinder (5). - An eccentric part (3e) formed eccentrically in a predetermined direction from the axis of the drive shaft (3b) of the drive means (3) is inserted into the roller (6), and the drive shaft (3b) is provided with main oil supply. A passage (13) is formed through the cylinder (5), and a head portion (7) is formed on both end surfaces of the cylinder (5).
), (8) are arranged and formed to form a compression chamber (9) between the inner peripheral surface of the cylinder (5) and the outer peripheral surface of the roller (6). is connected to a fluid suction passage (5a) and a fluid discharge passage (5d), and as the driving means (3) is driven, the roller (6) rotates within the cylinder (5) to In a rolling piston type compressor configured to suck fluid into a compression chamber (9) from a suction passage (5a) and compress the fluid, an eccentric portion (3e) of the drive shaft (3b) is provided with a hydraulic pressure supply path (14a) whose one end opens to the main oil supply path (13) and whose other end opens to the outer peripheral surface located in the eccentric direction of the eccentric portion (3e). A rolling ring characterized in that a low pressure passage (16) is provided that opens on the outer circumferential surface of the eccentric portion (3e) located in a direction opposite to the eccentric direction and whose other end opens to the suction passage (5a). Piston type compressor. 3. The rolling piston compressor according to claim 1 or 2, wherein one end is connected to the main oil supply passage (13).
an oil supply path (14) that opens at
b) is provided, and the other end opening of the oil supply path (14b) is provided with lubricating oil (
A rolling piston type compressor, characterized in that it is set at a position where the oil film reaction force of O) acts. 4. In the rolling piston compressor according to claim 3, the eccentric portion (3e) has an outer circumferential surface connected to the oil supply path (14b) and at least a hydraulic pressure supply path (14b).
a) A rolling piston type compressor characterized in that an oil supply groove (15) is formed extending toward a position diametrically opposed to the roller (6) with respect to the other end opening. [Claim 5] The roller according to claim 1, 2, 3 or 4.
In a ring piston type compressor, the hydraulic supply path (14a
), an eccentric part (3e) is cut out in a planar manner across both end surfaces, and hydraulic pressure is applied between the inner circumferential surface of the roller (6) and the eccentric part (3e). A rolling piston type compressor characterized in that a working space (A) is formed. 6. The rolling piston compressor according to claim 1, 2, 3, 4 or 5, wherein the eccentric portion (3e)
A rolling piston type compressor, characterized in that the end face of the head part (7), (8) is set at a position having a predetermined dimension.