Oil groove structure and compressor

Abstract

The invention relates to the technical field of compressors, in particular to an oil groove structure and a compressor comprising the oil groove structure. The oil groove structure comprises an oil guide groove used for storing lubricating oil, the oil guide groove is formed in the surface of the side, facing the air cylinder, of the cylinder cover, and the oil guide groove is provided with a front end close to the center of the cylinder cover and exposed out of the air cylinder and a rear end away from the center of the cylinder cover and communicated with the blade groove. The oil guide groove extends between the front end and the rear end in a bent and / or bent mode and is partially covered by the end face of the air cylinder. The contact surfaces of the blades, the piston and the cylinder cover can be effectively lubricated, so that the abrasion of the contact surfaces between the blades and the cylinder cover during reciprocating motion of the blades and rotation of the piston is reduced. Meanwhile, the oil guide groove is formed in the surface of the side, facing the air cylinder, of the cylinder cover, so that the contact area between the cylinder cover and the blades and the piston is reduced, the power of the compressor can be reduced, and efficiency is improved.

Description

Technical Field

[0001] The present invention relates to the technical field of compressors, and in particular to an oil groove structure and a compressor comprising the oil groove structure. Background Art

[0002] A rolling rotor compressor consists primarily of a motor, cylinder, upper and lower cylinder heads, a crankshaft, pistons, and blades. The crankshaft is driven by the motor to rotate, and the piston is mounted on the eccentric portion of the crankshaft. Driven by the eccentric portion, the piston rolls along the inner wall of the cylinder, forming a crescent-shaped working chamber between the outer circumference of the piston and the inner circumference of the cylinder. The sidewalls of the cylinder are provided with blade slots that accommodate the blades. The blade slots are connected to the crescent-shaped working chamber, allowing the blades to reciprocate within the slots. The blades' tips abut the outer circumference of the piston, dividing the crescent-shaped working chamber into a suction chamber and a compression chamber. The rotation of the eccentric portion of the crankshaft causes the radial position of the piston-blade contact point to change, causing the blades to reciprocate linearly within the slots between top dead center and bottom dead center. The top dead center is the position where the eccentric end of the eccentric portion is closest to the blade tip, while the bottom dead center is the position where the eccentric end of the eccentric portion is farthest from the blade tip. The upper and lower cylinder heads seal the cylinder's axial ends, with the upper and lower end surfaces of the vanes and piston in contact with the heads. When the compressor operates under harsh conditions, the reciprocating motion of the vanes and the rotation of the piston can easily cause wear on the contact surfaces between the vanes and piston and the heads, reducing compressor reliability and affecting performance. Summary of the Invention

[0003] In view of the above-mentioned defects of the prior art, the technical problem to be solved by the present invention is to provide an oil groove structure that can reduce the wear caused by the contact surface between the compressor blades and the cylinder head during reciprocating motion and rotation of the piston.

[0004] In order to solve the above technical problems, the present invention adopts the following technical solutions:

[0005] The present invention provides an oil groove structure for a compressor, the compressor including a cylinder, a cylinder head that closes the end of the cylinder, a piston that performs eccentric operation inside the cylinder, a vane groove formed on the cylinder, and a vane that performs linear reciprocating motion between an upper dead center and a lower dead center in the vane groove, the vane having a front end that abuts the piston and a rear end away from the piston, the oil groove structure including an oil guide groove for storing lubricating oil, the oil guide groove being formed on a side surface of the cylinder head facing the cylinder, the oil guide groove having a front end that is close to the center of the cylinder head and exposed to the inside of the cylinder, and a rear end that is away from the center of the cylinder head and connected to the vane groove, the oil guide groove extending in a curved and / or bent shape between the front end and the rear end and being partially covered by the end surface of the cylinder.

[0006] Preferably, when the blade is located at the bottom dead center, the rear end of the oil guide groove is exposed in the blade groove at the tail end of the blade.

[0007] Preferably, the portion of the oil guide groove exposed to the interior of the cylinder is located on one side of the center line of the blade groove.

[0008] Preferably, the tip of the oil guide groove extends from one side of the center line of the blade groove to the linear reciprocating motion path of the blade and does not exceed the center line of the blade groove.

[0009] Preferably, when the vane is located at the top dead center, the tip end of the oil guide groove is covered by the end surface of the piston and does not exceed the inner circumferential surface of the piston.

[0010] Preferably, the oil guide groove passes through the linear reciprocating motion path of the blade at least twice.

[0011] Preferably, the extended shape of the oil guide groove is any one or more combinations of C-shape, S-shape, W-shape, arc-shape, semicircular shape and arch-shape.

[0012] The present invention also provides a compressor comprising the oil tank structure described above.

[0013] Compared with the prior art, the present invention has significant improvements:

[0014] The present invention provides an oil guide groove on a side surface of the cylinder head facing the cylinder, with the front end of the oil guide groove exposed inside the cylinder, so that the piston passes through the front end of the oil guide groove during eccentric operation inside the cylinder, thereby lubricating the contact surface between the piston and the cylinder head by the lubricating oil stored in the oil guide groove; the rear end of the oil guide groove is connected to the vane groove, so that the vane passes through the rear end of the oil guide groove during linear reciprocating motion in the vane groove, thereby lubricating the contact surface between the vane and the cylinder head by the lubricating oil stored in the oil guide groove; the oil guide groove extends in a curved and / or bent shape between the front end and the rear end, thereby increasing the oil storage path of the oil guide groove and increasing the oil storage capacity, and the oil guide groove is partially covered by the end surface of the cylinder, which reduces the possibility of the lubricating oil stored in the oil guide groove escaping from the oil guide groove during operation of the compressor, so that the lubricating oil can be better stored in the oil guide groove, thereby ensuring the lubrication effect. Therefore, the oil groove structure of the present invention effectively lubricates the contact surfaces between the vanes and piston and the cylinder head, thereby reducing wear on the contact surfaces between the vanes and the cylinder head during reciprocating motion and the piston during rotation. Furthermore, the oil guide grooves on the cylinder head surface facing the cylinder reduce the contact area between the cylinder head, the vanes, and the piston, thereby reducing compressor power and improving efficiency. BRIEF DESCRIPTION OF THE DRAWINGS

[0015] Figure 1 This is a schematic diagram of the structure of the oil groove structure provided on the compressor according to an embodiment of the present invention, and the figure shows the state when the blade is at the bottom dead center.

[0016] Figure 2 yes Figure 1 Axial side view.

[0017] Figure 3 This is a schematic diagram of the structure of the oil groove structure provided on the compressor according to an embodiment of the present invention, and the figure shows the state when the blade is at the top dead center.

[0018] Figure 4 yes Figure 3 Axial side view.

[0019] The description of the accompanying drawings is as follows:

[0020] 1 cylinder

[0021] 1a Inner surface of the cylinder

[0022] 2 cylinder heads

[0023] 3 pistons

[0024] 3a Inner surface of the piston

[0025] 3b Outer surface of the piston

[0026] 4 blade slots

[0027] 4a Centerline

[0028] 5 blades

[0029] 51 Front-end

[0030] 52 tail end

[0031] 6 Crankshaft

[0032] 60 long axis segment

[0033] 61 eccentric part

[0034] 61a Outer peripheral surface of the eccentric portion

[0035] 10 Oil guide groove

[0036] 101 Pioneer

[0037] 102 Backend DETAILED DESCRIPTION

[0038] The following is a further detailed description of the specific embodiments of the present invention in conjunction with the accompanying drawings. These embodiments are only used to illustrate the present invention, and are not intended to limit the present invention.

[0039] In the description of the present invention, it should be noted that the terms "center," "longitudinal," "lateral," "upper," "lower," "front," "back," "left," "right," "vertical," "horizontal," "top," "bottom," "inner," and "outer" and the like, indicating orientations or positional relationships, are based on the orientations or positional relationships shown in the accompanying drawings and are intended solely to facilitate and simplify the description of the present invention. They are not intended to indicate or imply that the devices or components referred to must have, be constructed, or operate in a specific orientation, and therefore should not be construed as limiting the present invention. Furthermore, the terms "first" and "second" are used for descriptive purposes only and should not be construed as indicating or implying relative importance.

[0040] In the description of the present invention, it should be noted that, unless otherwise expressly specified or limited, the terms "mounted," "connected," and "connected" should be understood in a broad sense. For example, they may refer to fixed, detachable, or integral connections; mechanical or electrical connections; direct or indirect connections through an intermediate medium; and internal communication between two components. Those skilled in the art will understand the specific meanings of the above terms in the present invention based on specific circumstances.

[0041] Furthermore, in the description of the present invention, unless otherwise specified, “plurality” means two or more.

[0042] like Figures 1 to 4The figure shows an embodiment of the oil groove structure provided by the present invention. The oil groove structure of this embodiment is used in a compressor, which includes a cylinder 1, a cylinder head 2, a piston 3, a vane groove 4, a vane 5, and a crankshaft 6. The cylinder 1 is an axially continuous cylinder structure. The cylinder head 2 seals the ends of the cylinder 1. The cylinder 1 is sealed at both ends along the axial direction by the cylinder head 2 to form a closed cavity. The center of the cylinder head 2 is located on the axis of the cylinder 1, that is, the cylinder head 2 and the cylinder 1 are arranged coaxially. The crankshaft 6 has a long shaft section 60 connected to the motor rotor and an eccentric portion 61 eccentrically arranged relative to the long shaft section 60. The long shaft section 60 of the crankshaft 6 is arranged coaxially with the cylinder 1, and the eccentric portion 61 of the crankshaft 6 is placed in the cavity inside the cylinder 1. The piston 3 operates eccentrically inside the cylinder 1. The piston 3 is sleeved on the eccentric portion 61 of the crankshaft 6, and the inner circumferential surface 3a of the piston abuts the outer circumferential surface 61a of the eccentric portion. When the motor drives the crankshaft 6 to rotate, the eccentric portion 61 of the crankshaft 6 drives the piston 3 to perform eccentric rotational motion within the cavity of the cylinder 1, causing the piston 3 to roll along the inner wall of the cylinder 1, forming a crescent-shaped working chamber between the piston's outer circumferential surface 3b and the cylinder's inner circumferential surface 1a. A vane groove 4 is defined in the sidewall of the cylinder 1. The vane groove 4 communicates with the cavity within the cylinder 1 and extends radially along the cylinder 1. The vane groove 4 accommodates a vane 5, whose centerline coincides with the centerline 4a of the vane groove 4. The vane 5 performs linear reciprocating motion within the vane groove 4 between the top dead center and the bottom dead center. The vane 5 has a front end 51 that abuts the piston 3 and a rear end 52 that is spaced away from the piston 3. The front end 51 of the vane 5 abuts the piston's outer circumferential surface 3b, and the front end 51 of the vane 5 has a convex arc-shaped end surface. The blade 5 is in the shape of an elongated strip extending along the axial direction of the piston 3 and covers the outer peripheral surface 3b of the piston in the axial direction of the piston 3. Thus, the blade 5 divides the crescent-shaped working chamber between the outer peripheral surface 3b of the piston and the inner peripheral surface 1a of the cylinder into two independent chambers, which serve as the suction chamber and the compression chamber respectively. When the piston 3 rotates eccentrically in the cavity inside the cylinder 1, the radial position of the point where the front end 51 of the blade 5 contacts the outer peripheral surface 3b of the piston changes, causing the blade 5 to perform linear reciprocating motion in the blade groove 4. Figure 1 and Figure 2 As shown, when the crankshaft 6 rotates until the eccentric end of the eccentric portion 61 is farthest from the front end 51 of the blade 5, the position of the blade 5 is the bottom dead center. Figure 3 and Figure 4 As shown, when the crankshaft 6 rotates until the eccentric end of the eccentric portion 61 is closest to the front end 51 of the blade 5, the position of the blade 5 is the top dead center.

[0043] The oil groove structure of this embodiment includes an oil guide groove 10 for storing lubricating oil. The oil guide groove 10 is formed on the side of the cylinder head 2 facing the cylinder 1. The oil guide groove 10 has a tip 101 near the center of the cylinder head 2 and a rear end 102 away from the center of the cylinder head 2. The tip 101 of the oil guide groove 10 is exposed within the cylinder 1. That is, the tip 101 of the oil guide groove 10 extends toward the center of the cylinder head 2 and beyond the inner circumferential surface 1a of the cylinder. This allows the piston 3 to pass through the tip 101 of the oil guide groove 10 during eccentric rotation within the cylinder 1, thereby lubricating the contact surface between the piston 3 and the cylinder head 2 with the lubricating oil stored in the oil guide groove 10. The rear end 102 of the oil guide groove 10 is connected to the vane groove 4. This allows the vane 5 to pass through the rear end 102 of the oil guide groove 10 during linear reciprocating motion within the vane groove 4, thereby lubricating the contact surface between the vane 5 and the cylinder head 2 with the lubricating oil stored in the oil guide groove 10. The oil guide groove 10 extends in a curved and / or zigzag shape between the front end 101 and the rear end 102, thereby increasing the oil storage path of the oil guide groove 10 and the oil storage capacity. Furthermore, the oil guide groove 10 is partially covered by the end surface of the cylinder 1, thereby reducing the amount of lubricating oil stored in the oil guide groove 10 from escaping from the oil guide groove 10 during compressor operation, allowing the lubricating oil to be better stored in the oil guide groove 10 to ensure lubrication. Thus, the oil groove structure of this embodiment can effectively lubricate the contact surfaces between the vanes 5 and the piston 3 and the cylinder head 2, thereby reducing wear on the contact surfaces between the vanes 5 and the piston 3 and the cylinder head 2 during reciprocating motion. Furthermore, since the oil guide groove 10 is provided on the side of the cylinder head 2 facing the cylinder 1, the contact area between the cylinder head 2 and the vanes 5 and piston 3 is reduced, thereby reducing compressor power and improving efficiency.

[0044] See also Figure 2 In this embodiment, preferably, when the blade 5 is at the bottom dead center, the rear end 102 of the oil guide groove 10 is exposed in the blade groove 4 at the tail end 52 of the blade 5. Thus, lubricating oil can be introduced into the oil guide groove 10 from the rear end 102 of the oil guide groove 10, thereby supplying the lubricating oil stored in the oil guide groove 10 and ensuring that the amount of lubricating oil in the oil guide groove 10 is sufficient.

[0045] like Figure 2 As shown, the dimension of the blade 5 extending radially along the cylinder 1 is L1, and when the blade 5 is at the bottom dead center, the minimum radial distance between the front end 51 of the blade 5 and the outer peripheral surface 3b of the piston and the center of the cylinder 1 is L2, and the maximum radial distance between the rear end 102 of the oil guide groove 10 and the center of the cylinder 1 is Lmax, and satisfies: Lmax>L1+L2, so that when the blade 5 is at the bottom dead center, the rear end 102 of the oil guide groove 10 is exposed at the tail end 52 of the blade 5 in the blade groove 4.

[0046] See also Figure 2 and Figure 4In this embodiment, because the tip 101 of the oil guide groove 10 is exposed inside the cylinder 1, a portion of the oil guide groove 10 is exposed inside the cylinder 1. Preferably, the portion of the oil guide groove 10 exposed inside the cylinder 1 is located to one side of the centerline 4a of the vane groove 4. This prevents the portion of the oil guide groove 10 exposed inside the cylinder 1 from connecting the suction chamber and the compression chamber separated by the vanes 5 during the eccentric rotation of the piston 3 inside the cylinder 1 and the linear reciprocating motion of the vanes 5 in the vane groove 4, thereby preventing leakage.

[0047] Preferably, the tip 101 of the oil guide groove 10 extends from one side of the centerline 4a of the vane groove 4 to the linear reciprocating path of the vane 5, and the tip 101 of the oil guide groove 10 does not exceed the centerline 4a of the vane groove 4. This ensures that the vane 5 will pass through the tip 101 of the oil guide groove 10 during its linear reciprocating motion in the vane groove 4. The vane 5 passes both the rear end 102 and the tip 101 of the oil guide groove 10 during its linear reciprocating motion in the vane groove 4, facilitating lubrication of the entire contact surface between the vane 5 and the cylinder head 2 using the lubricating oil stored in the oil guide groove 10. Since the end surface of the front end 51 of the blade 5 is a convex arc surface, the end surface of the front end 51 of the blade 5 is in linear contact with the outer peripheral surface 3b of the piston. The contact line is located on the axial plane of the center line 4a of the blade groove 4 of the cylinder 1. The tip 101 of the oil guide groove 10 does not exceed the center line 4a of the blade groove 4. It can be ensured that when the front end 51 of the blade 5 passes through the tip 101 of the oil guide groove 10, the tip 101 of the oil guide groove 10 will not connect the suction chamber and the compression chamber separated by the blade 5.

[0048] like Figure 4 As shown, the extension dimension of the blade 5 in the direction perpendicular to the axial plane of the center line 4a of the vane groove 4 of the cylinder 1 (i.e., the thickness of the blade 5) is D, and the maximum extension dimension of the tip 101 of the oil guide groove 10 located on the linear reciprocating motion path of the blade 5 in the direction perpendicular to the axial plane of the center line 4a of the vane groove 4 of the cylinder 1 is d, and satisfies: d<D / 2, so as to achieve that the tip 101 of the oil guide groove 10 does not exceed the center line 4a of the vane groove 4.

[0049] See also Figure 4In this embodiment, preferably, when the vane 5 is at top dead center, the tip 101 of the oil guide groove 10 is covered by the end surface of the piston 3, and the tip 101 of the oil guide groove 10 does not extend beyond the inner circumferential surface 3a of the piston. When the vane 5 is at top dead center, the tip 101 of the oil guide groove 10 is covered by the end surface of the piston 3, ensuring that the piston 3 passes through the tip 101 of the oil guide groove 10 during eccentric rotation within the cylinder 1. Thus, the tip 101 of the oil guide groove 10 supplies oil to the contact surface between the piston 3 and the cylinder head 2 for lubrication. Since the axial dimension of the piston 3 mounted on the eccentric portion 61 of the crankshaft 6 is larger than the axial dimension of the eccentric portion 61, both axial ends of the piston 3 protrude relative to the eccentric portion 61 to form a gap between the piston 3 and the crankshaft 6. When the blade 5 is located at the top dead center, the tip 101 of the oil guide groove 10 does not exceed the inner circumferential surface 3a of the piston, thereby ensuring that the tip 101 of the oil guide groove 10 will not be connected to the gap space formed between the piston 3 and the crankshaft 6 during the eccentric operation of the piston 3 inside the cylinder 1, thereby preventing leakage.

[0050] like Figure 4 As shown, the radius of the cylinder's inner circumferential surface 1a is R, and the minimum radial distance between the tip 101 of the oil guide groove 10 and the center of the cylinder 1 is Lmin, satisfying the following relationship: Lmin < R. This ensures that the tip 101 of the oil guide groove 10 is exposed within the cylinder 1, so that when the vane 5 is at top dead center, the tip 101 of the oil guide groove 10 is covered by the end surface of the piston 3. When the vane 5 is at top dead center, the maximum radial distance between the piston's inner circumferential surface 3a and the center of the cylinder 1 is L3. The minimum radial distance Lmin between the tip 101 of the oil guide groove 10 and the center of the cylinder 1 satisfies the following relationship: Lmin > L3, ensuring that the tip 101 of the oil guide groove 10 does not extend beyond the piston's inner circumferential surface 3a.

[0051] In this embodiment, preferably, the oil guide groove 10 extending in a curved and / or bent shape between the front end 101 and the rear end 102 passes through the linear reciprocating motion path of the blade 5 at least twice, so as to increase the oil supply of the oil guide groove 10 to the contact surface between the blade 5 and the cylinder head 2, thereby enhancing the lubrication effect.

[0052] In this embodiment, preferably, the extension shape of the oil guide groove 10 between the front end 101 and the rear end 102 can be any one or more combinations of C-shape, S-shape, W-shape, arc-shape, semicircular shape and arch-shape. Figure 2 and Figure 4 Type C is taken as an example.

[0053] Based on the oil tank structure of the present invention, an embodiment of the present invention further provides a compressor. The compressor of this embodiment includes the oil tank structure of this embodiment.

[0054] The above is only a preferred embodiment of the present invention. It should be pointed out that for ordinary technicians in this technical field, several improvements and substitutions can be made without departing from the technical principles of the present invention. These improvements and substitutions should also be regarded as the scope of protection of the present invention.

Claims

1. An oil tank structure for a compressor, comprising a cylinder (1), a cylinder head (2) sealing an end of the cylinder (1), a piston (3) operating eccentrically within the cylinder (1), a vane groove (4) provided on the cylinder (1), and a vane (5) performing linear reciprocating motion between an upper dead center and a lower dead center within the vane groove (4), wherein the vane (5) has a front end (51) abutting against the piston (3) and a rear end (52) away from the piston (3), characterized in that: The oil groove structure comprises an oil guide groove (10) for storing lubricating oil. The oil guide groove (10) is opened on a side surface of the cylinder head (2) facing the cylinder (1). The oil guide groove (10) has a front end (101) close to the center of the cylinder head (2) and exposed to the inside of the cylinder (1) and a rear end (102) away from the center of the cylinder head (2) and connected to the blade groove (4). The oil guide groove (10) extends in a curved and / or bent shape between the front end (101) and the rear end (102) and is partially covered by the end surface of the cylinder (1).

2. The oil tank structure according to claim 1, characterized in that: When the blade (5) is located at the bottom dead center, the rear end (102) of the oil guide groove (10) is exposed in the blade groove (4) to the tail end (52) of the blade (5).

3. The oil tank structure according to claim 1, characterized in that: The portion of the oil guide groove (10) exposed inside the cylinder (1) is located on one side of the center line of the blade groove (4).

4. The oil tank structure according to claim 3, characterized in that: The tip (101) of the oil guide groove (10) extends from one side of the center line of the blade groove (4) to the linear reciprocating motion path of the blade (5) and does not exceed the center line of the blade groove (4).

5. The oil tank structure according to claim 1, characterized in that: When the blade (5) is located at the top dead center, the tip (101) of the oil guide groove (10) is covered by the end surface of the piston (3) and does not exceed the inner circumferential surface of the piston (3).

6. The oil tank structure according to claim 1, characterized in that: The oil guide groove (10) passes through the linear reciprocating motion path of the blade (5) at least twice.

7. The oil tank structure according to claim 1, characterized in that: The extended shape of the oil guide groove (10) is any one or more combinations of C-type, S-type, W-type, arc-type, semicircular-type and arch-type.

8. A compressor, characterized in that: Comprising the oil tank structure according to any one of claims 1 to 7.

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