Twin-cylinder compressor

Abstract

The present invention discloses a twin-cylinder compressor, comprising: a motor, a crankshaft, a first cylinder and a second cylinder; a first blade, one end of which abuts against a first rotary piston, dividing the first cylinder into a first suction chamber and a first exhaust chamber; a second blade, one end of which abuts against a second rotary piston, dividing the second cylinder into a second suction chamber and a second exhaust chamber, the volumes of the first suction chamber and the second suction chamber are equal, and the volumes of the first exhaust chamber and the second exhaust chamber are equal; the first cylinder is provided with a first suction pipeline, one end of the first suction pipeline is connected to the first suction chamber, and the other end is connected to a first liquid storage chamber through a first intake pipe, and the second cylinder is provided with a second suction pipeline, one end of the second suction pipeline is connected to the second suction chamber, and the other end is connected to a second liquid storage chamber through a second intake pipe.

Description

Technical Field

[0001] The present invention relates to the field of air conditioning and refrigeration, and more particularly to a dual-cylinder compressor. Background Art

[0002] Existing twin-cylinder compressors include two cylinders: an upper cylinder and a lower cylinder. The upper cylinder includes an intake chamber and a discharge chamber, while the lower cylinder also includes an intake chamber and a discharge chamber. During refrigerant compression, the refrigerant is drawn into the intake chamber and discharged from the discharge chamber. However, during compression, the volumes of the upper and lower cylinder intake and discharge chambers differ. This results in a greater combined force on the compressor's crankshaft, causing significant bending deformation of the crankshaft. This in turn increases or decreases the clearances between the various components of the compressor pump body, reducing the compressor's reliability. Summary of the Invention

[0003] In response to the problems existing in the prior art, the purpose of the present invention is to provide a two-cylinder compressor. The two-cylinder compressor of the present invention reduces the volume difference between the two suction chambers and the volume difference between the two exhaust chambers, thereby reducing the resultant force on the lower end part of the compressor crankshaft, thereby reducing the winding of the lower end part of the compressor crankshaft, thereby reducing the crankshaft diameter of the two-cylinder compressor in the present invention.

[0004] According to one aspect of the present invention, there is provided a twin-cylinder compressor, comprising:

[0005] The motor, the first cylinder and the second cylinder are all accommodated in the housing;

[0006] a crankshaft, one end of which is connected to the motor, and the other end of which is connected to a first rotary piston disposed in the first cylinder and a second rotary piston disposed in the second cylinder;

[0007] a first blade, one end of which abuts against the first rotary piston to divide the first cylinder into a first intake chamber and a first exhaust chamber;

[0008] a second blade, one end of which abuts against the second rotary piston, dividing the second cylinder into a second intake chamber and a second exhaust chamber;

[0009] The first cylinder is provided with a first intake pipe, one end of which is connected to the first intake chamber, and the other end is connected to a first liquid storage chamber through a first intake pipe. The second cylinder is provided with a second intake pipe, one end of which is connected to the second intake chamber, and the other end is connected to a second liquid storage chamber through a second intake pipe. The angle between the projection vector of the intake direction vector of the first intake pipe on the reference plane and the projection vector of the intake direction vector of the second intake pipe on the reference plane is in the range of [5°, 180°].

[0010] Preferably, the first cylinder is provided with a first exhaust pipe, the two ends of the first exhaust pipe are respectively connected to the first exhaust chamber and the internal space of the shell, the second cylinder is provided with a second exhaust pipe, the two ends of the second exhaust pipe are respectively connected to the second exhaust chamber and the internal space of the shell, and the angle between the projection vector of the exhaust direction vector of the first exhaust pipe on a reference plane perpendicular to the central axis of the crankshaft and the projection vector of the exhaust direction vector of the second exhaust pipe on the reference plane is in the range of [5°, 180°].

[0011] Preferably, the volumes of the first suction chamber and the second suction chamber are equal, and the volumes of the first exhaust chamber and the second exhaust chamber are equal.

[0012] Preferably, a cross-sectional shape of the first intake chamber along the radial direction of the crankshaft and a cross-sectional shape of the second intake chamber along the radial direction of the crankshaft are symmetrical based on the axis center of the crankshaft;

[0013] A cross-sectional shape of the first exhaust chamber along the radial direction of the crankshaft and a cross-sectional shape of the second exhaust chamber along the radial direction of the crankshaft are symmetrical about an axis of the crankshaft.

[0014] Preferably, the first liquid storage chamber is a first liquid reservoir, and the second liquid storage chamber is a second liquid reservoir.

[0015] Preferably, the first liquid reservoir and the second liquid reservoir are arranged in sequence along the radial direction of the shell.

[0016] Preferably, the first liquid reservoir and the second liquid reservoir are on the same side of the housing.

[0017] Preferably, the first liquid reservoir and the second liquid reservoir are respectively located on both sides of the shell.

[0018] Preferably, the first liquid storage chamber and the second liquid storage chamber are the same liquid reservoir.

[0019] Preferably, the first liquid storage chamber and the second liquid storage chamber are two separated independent inner chambers in a third liquid reservoir.

[0020] The beneficial effect of the above technical solution is that the twin-cylinder compressor of the present invention reduces the resultant force on the lower end part of the compressor crankshaft by reducing the volume difference between the two suction chambers and the volume difference between the two exhaust chambers, thereby reducing the winding of the lower end part of the compressor crankshaft, thereby reducing the crankshaft diameter of the twin-cylinder compressor in the present invention.

[0021] Other features and advantages of the present invention, as well as the structure and operation of various embodiments of the present invention, will be described in detail below with reference to the accompanying drawings. It should be noted that the present invention is not limited to the specific embodiments described herein. These embodiments are provided herein for illustrative purposes only. BRIEF DESCRIPTION OF THE DRAWINGS

[0022] Other features, objects and advantages of the present invention will become more apparent from the following detailed description of non-limiting embodiments with reference to the accompanying drawings.

[0023] Figure 1 This is a structural diagram of a twin-cylinder compressor in Example 1 in a preferred embodiment of the present invention;

[0024] Figure 2 This is a structural diagram of a twin-cylinder compressor in Example 2, a preferred embodiment of the present invention;

[0025] Figure 3 This is a schematic structural diagram of a twin-cylinder compressor in Example 3 in a preferred embodiment of the present invention;

[0026] Figure 4 This is a schematic transverse cross-sectional view of the first cylinder in Example 1 in a preferred embodiment of the present invention;

[0027] Figure 5 This is a schematic transverse cross-sectional view of the second cylinder in Example 1 in a preferred embodiment of the present invention;

[0028] Figure 6 A comparison diagram of the resultant force acting on the crankshaft in a preferred embodiment of the present invention; and

[0029] Figure 7 This is a comparison diagram of crankshaft bending in a preferred embodiment of the present invention.

[0030] List of reference numerals:

[0031] 101 Twin Cylinder Compressor

[0032] 102 housing

[0033] 103 Motor

[0034] 104 First Cylinder

[0035] 105 Second Cylinder

[0036] 106 Upper cylinder head

[0037] 107 Lower cylinder head

[0038] 108 middle partition

[0039] 109 Crankshaft

[0040] 110 upper muffler

[0041] 111 lower muffler

[0042] 112 First rotary piston

[0043] 113 Second rotary piston

[0044] 114 First Leaf

[0045] 115 Second Leaf

[0046] 116 Third Reservoir

[0047] 117 First Inhalation Chamber

[0048] 118 First exhaust chamber

[0049] 119 Second suction chamber

[0050] 120 Second exhaust chamber

[0051] 121 First Liquid Reservoir

[0052] 122 Second liquid reservoir

[0053] 123 First intake pipe

[0054] 124 Second intake pipe

[0055] 125 First suction line

[0056] 126 Second suction line

[0057] 127 First exhaust pipe

[0058] 128 Second exhaust pipe

[0059] The features and advantages of the present invention will become more apparent from the following detailed description taken in conjunction with the accompanying drawings. Throughout the accompanying drawings, the same figures identify corresponding elements. In the accompanying drawings, the same reference numerals generally indicate the same, functionally similar and / or structurally similar elements. DETAILED DESCRIPTION

[0060] The following will clearly and completely describe the technical solutions in the embodiments of the present invention in conjunction with the accompanying drawings. Obviously, the described embodiments are only part of the embodiments of the present invention, not all of the embodiments. Based on the embodiments of the present invention, all other embodiments obtained by ordinary technicians in this field without making any creative efforts shall fall within the scope of protection of the present invention.

[0061] The words "first", "second" and similar terms used in this disclosure do not indicate any order, quantity or importance, but are only used to distinguish different components. Words such as "include" or "comprise" mean that the elements or objects preceding the word include the elements or objects listed after the word and their equivalents, without excluding other elements or objects. Words such as "connect" or "connected" are not limited to physical or mechanical connections, but may include electrical connections, whether direct or indirect. "Up", "down", "left", "right" and the like are only used to indicate relative positional relationships. When the absolute position of the object being described changes, the relative positional relationship may also change accordingly.

[0062] It should be noted that, in the absence of conflict, the embodiments of the present invention and the features in the embodiments may be combined with each other.

[0063] The present invention will be further described below with reference to the accompanying drawings and specific embodiments, but they are not intended to limit the present invention.

[0064] Example 1

[0065] refer to Figure 1 , Figure 1 This is a schematic diagram of the structure of a two-cylinder compressor in Example 1. This embodiment provides a two-cylinder compressor 101, which includes a motor 103, a first cylinder 104, and a second cylinder 105. The motor 103, the first cylinder 104, and the second cylinder 105 are all housed in a housing 102. The two-cylinder compressor 101 in this embodiment is a vertical compressor. The first cylinder 104 is located above the second cylinder 105. That is, the first cylinder 104 is the upper cylinder in this embodiment, and the second cylinder 105 is the lower cylinder in this embodiment.

[0066] Reference Attachment Figure 1. The shell 102 also includes a vertically arranged crankshaft 109, the upper end of the crankshaft 109 is connected to the rotor of the motor 103, and the lower end of the crankshaft 109 is connected to the first rotary piston 112 and the second rotary piston 113. The first rotary piston 112 is located in the first cylinder 104, that is, the upper piston in this embodiment, and the second rotary piston 113 is located in the second cylinder 105, that is, the lower piston in this embodiment. The crankshaft 109 transmits the rotational force of the motor 103 to the first rotary piston 112 and the second rotary piston 113 respectively, causing them to rotate in the first cylinder 104 and the second cylinder 105 respectively to compress the refrigerant. For example, the outer stator of the motor 103 is fixed to the inner wall of the shell 102, and the rotor of the motor 103 is sleeved on the upper end of the crankshaft 109. The rotor is clamped and drives the crankshaft 109 by cold pressing, but this is not limited to this. The rotor can also be fixed to the crankshaft 109 by heat sleeve or bonding. The rotor rotates relative to the stator to transmit the rotational force of the motor 103 to the first rotary piston 112 in the first cylinder 104 and the second rotary piston 113 in the second cylinder 105 to compress the refrigerant.

[0067] An upper cylinder head 106 is located above the first cylinder 104, and a lower cylinder head 107 is located below the second cylinder 105. A middle diaphragm 108 is located between the upper and lower cylinder heads 106, 107. An upper muffler 110 is located above the upper cylinder head 106, and a lower muffler 111 is located below the lower cylinder head 107. The upper cylinder head 106, the first cylinder 104, and the middle diaphragm 108 form a first compression space for compressing refrigerant. A second compression space for compressing refrigerant is formed between the lower cylinder head 107, the second cylinder 105, and the middle diaphragm 108.

[0068] Reference Attachment Figure 4 and attached Figure 5 , Figure 4 and Figure 5The positions of the first rotary piston 112 in the first cylinder 104 and the second rotary piston 113 in the second cylinder 105 at the same time are shown. The centers of the first and second rotary pistons 112, 113 are symmetrical about the centerline of the crankshaft 109. A first vane 114 is provided through the sidewall of the first cylinder 104, while a second vane 115 is provided through the sidewall of the second cylinder 105. One end of the first vane 114 abuts against the first rotary piston 112, dividing the first compression space into a first intake chamber 117 and a first exhaust chamber 118. One end of the second vane 115 abuts against the second rotary piston 113, dividing the second compression space into a second intake chamber 119 and a second exhaust chamber 120. A first intake line 125 and a first exhaust line 127 are provided through the sidewall of the first cylinder 104. For example, the first intake line 125 and the first exhaust line 127 can be arranged symmetrically around the first vane 114. A second intake line 126 and a second exhaust line 128 are formed on a side wall of the second cylinder 105 . The first intake line 125 and the second exhaust line 128 may be symmetrically arranged based on the second blade 115 .

[0069] The angle between the projection vector of the exhaust direction vector of the first exhaust pipe 127 on a reference plane and the projection vector of the exhaust direction vector of the second exhaust pipe 128 on the reference plane is in the range of [5°, 180°]. The angle between the projection vector of the intake direction vector of the first intake pipe 125 on the reference plane and the projection vector of the intake direction vector of the second intake pipe 126 on the reference plane is in the range of [5°, 180°]. The reference plane is any plane perpendicular to the center line of the crankshaft 109. In this embodiment, the lower end surface of the shell is used as the reference plane. The exhaust direction vector is parallel to the axis of the first exhaust pipe 127 or the second exhaust pipe 128 and its direction indicates the discharge direction of the refrigerant. Similarly, the intake direction vector is parallel to the first intake pipe 125 or the second intake pipe 126 and its direction indicates the suction direction of the refrigerant.

[0070] refer to Figure 4 and Figure 5 At any moment when the crankshaft 109 drives the first rotary piston 112 and the second rotary piston 113 to rotate, Figure 4 The first suction chamber 117 and Figure 5 The volumes of the second suction chamber 119 are equal, that is, the volumes of the first suction chamber 117 in the first cylinder 104 and the second suction chamber 119 in the second cylinder 105 are equal. At any moment when the crankshaft 109 drives the first rotary piston 112 and the second rotary piston 113 to rotate, Figure 4 The first exhaust chamber 118 and Figure 5The volumes of the second exhaust chamber 120 are shown to be equal, that is, the volumes of the first exhaust chamber 118 in the first cylinder 104 and the second exhaust chamber 120 in the second cylinder 105 are equal. This effectively reduces the combined force at the lower end of the crankshaft 109, particularly the portion of the crankshaft 109 located within the first cylinder 104 and the second cylinder 105, thereby reducing the winding of this portion. This results in a smaller diameter of the crankshaft 109 in this embodiment than in conventional compressors.

[0071] In some embodiments, when the included angle between the projection vector of the exhaust direction vector of the first exhaust line 127 on a reference plane and the projection vector of the exhaust direction vector of the second exhaust line 128 on the reference plane varies within the range of [5°, 180°], the first exhaust chamber 118 and the second exhaust chamber 120 may be unequal. When the included angle between the projection vector of the intake direction vector of the first intake line 125 on the reference plane and the projection vector of the intake direction vector of the second intake line 126 on the reference plane varies within the range of [5°, 180°], the first intake chamber 117 and the second intake chamber 119 may be unequal.

[0072] In this embodiment, the shape of the radial cross-section of the first intake chamber 117 along the crankshaft 109 and the shape of the radial cross-section of the second intake chamber 119 along the crankshaft 109 are symmetrical about the center line of the crankshaft 109, and the shape of the radial cross-section of the first exhaust chamber 118 along the crankshaft 109 and the shape of the radial cross-section of the second exhaust chamber 120 along the crankshaft 109 are symmetrical about the center line of the crankshaft 109. Figure 4 and Figure 5 The straight line X1X2 and the straight line Y1Y2 divide the first cylinder 104 and the second cylinder 105 into four parts. The intersection of the straight line X1X2 and the straight line Y1Y2 is the center point of the crankshaft 109 (the point on the center axis). The first exhaust chamber 118 and the second exhaust chamber 120 are symmetrical about the center point of the crankshaft 109, and the first intake chamber 117 and the second intake chamber 119 are also symmetrical about the center point of the crankshaft 109.

[0073] Furthermore, the first intake conduit 125 and the second intake conduit 126 may also be centrosymmetrical about the centerline of the crankshaft 109, i.e., the angle between the first intake conduit 125 and the second intake conduit 126 is 180°, the axial direction of the first intake conduit 125 and the axial direction of the second intake conduit 126 are parallel, and the intake directions are opposite. The ends of the first exhaust conduit 127 are connected to the first exhaust chamber 118 and the interior space of the housing 102, respectively. The ends of the second exhaust conduit 128 are connected to the second exhaust chamber 120 and the interior space of the housing 102, respectively. The second exhaust conduit 128 and the first exhaust conduit 127 may also be centrosymmetrical about the centerline of the crankshaft 109, the angle between the first exhaust conduit 127 and the second exhaust conduit 128 is 180°, the axial direction of the first exhaust conduit 127 and the axial direction of the second exhaust conduit 128 are parallel, and the intake directions are opposite. In this arrangement, the lower end of the crankshaft 109 is effectively reduced, so that the resultant force of the portion of the crankshaft 109 located in the first cylinder 104 and the second cylinder 105 is minimized, and the twist is also minimized.

[0074] refer to Figure 6 and Figure 7 When the first exhaust chamber 118 and the second exhaust chamber 120 are symmetrical about the center line of the crankshaft 109, and the first intake chamber 117 and the second intake chamber 119 are also symmetrical about the center line of the crankshaft 109, the resultant force of the refrigerant in the first intake chamber 117, the second intake chamber 119, the first exhaust chamber 118, and the second exhaust chamber 120 on the crankshaft 109 is almost zero, and the winding of this section of the crankshaft 109 also fluctuates around 0, while the winding of the existing compressor obviously has a peak value, which makes the diameter of the crankshaft 109 in this embodiment smaller than that of the crankshaft in the existing compressor.

[0075] refer to Figure 1 . The two ends of the first suction pipe 125 are respectively connected to the first suction chamber 117 and the first air inlet pipe 123, and the two ends of the second suction pipe 126 are respectively connected to the second suction chamber 119 and the second air inlet pipe 124. The refrigerant enters the first suction chamber 117 and the second suction chamber 119 through the first air inlet pipe 123 and the second air inlet pipe 124 respectively. The other end of the first air inlet pipe 123 is connected to the first liquid storage chamber, and the other end of the second air inlet pipe 124 is connected to the second liquid storage chamber. In this embodiment, the first liquid storage chamber (not shown in the figure) and the second liquid storage chamber (not shown in the figure) are both located in the third liquid reservoir 116, that is, the third liquid reservoir 116 includes the first liquid storage chamber and the second liquid storage chamber. The first liquid storage chamber and the second liquid storage chamber can be two separated independent inner chambers in the third liquid reservoir 116, respectively.

[0076] Example 2

[0077] like Figure 2As shown, in a variation of Example 1, the first liquid storage chamber and the second liquid storage chamber may be a first liquid reservoir 121 and a second liquid reservoir 122 arranged side by side. The volume of the first liquid reservoir 121 and the volume of the second liquid reservoir 122 may be the same. The bottom of the first liquid reservoir 121 supplies refrigerant to the first suction chamber 117 via a first air inlet pipe 123, and the bottom of the second liquid reservoir 122 supplies refrigerant to the second suction chamber 119 via a second air inlet pipe 124. The first liquid reservoir 121 and the second liquid reservoir 122 are arranged sequentially along the radial direction of the housing 102.

[0078] Example 3

[0079] like Figure 3 As shown, in a variation of Example 1, the first liquid storage chamber and the second liquid storage chamber may be a first liquid reservoir 121 and a second liquid reservoir 122, respectively arranged on both sides of the housing 102. The volume of the first liquid reservoir 121 and the volume of the second liquid reservoir 122 may be the same. The bottom of the first liquid reservoir 121 supplies refrigerant to the first suction chamber 117 through a first air inlet pipe 123, and the bottom of the second liquid reservoir 122 supplies refrigerant to the second suction chamber 119 through a second air inlet pipe 124.

[0080] Preferably, the first liquid reservoir 121 and the second liquid reservoir 122 have the same volume and are symmetrical based on the crankshaft 109, which can effectively offset the axial and radial vibrations caused by the intake air.

[0081] In summary, the twin-cylinder compressor of the present invention reduces the resultant force received by the lower end portion of the compressor crankshaft by setting two intake chambers of equal volume and two exhaust chambers of equal volume, thereby reducing the winding of the lower end portion of the compressor crankshaft, thereby reducing the crankshaft diameter of the twin-cylinder compressor in the present invention.

[0082] The above is a further detailed description of the present invention in conjunction with specific preferred embodiments, and the specific implementation of the present invention should not be considered to be limited to these descriptions. For those skilled in the art to which the present invention belongs, several simple deductions or substitutions can be made without departing from the concept of the present invention, and all of these should be considered to fall within the scope of protection of the present invention.

Claims

1. A twin-cylinder compressor, characterized in that: include: The motor, the first cylinder and the second cylinder are all accommodated in the housing; a crankshaft, one end of which is connected to the motor, and the other end of which is connected to a first rotary piston disposed in the first cylinder and a second rotary piston disposed in the second cylinder; a first blade, one end of which abuts against the first rotary piston to divide the first cylinder into a first intake chamber and a first exhaust chamber; a second blade, one end of which abuts against the second rotary piston, dividing the second cylinder into a second intake chamber and a second exhaust chamber; The first cylinder is provided with a first intake pipe, one end of the first intake pipe is connected to the first intake chamber, and the other end is connected to a first liquid storage chamber via a first intake pipe. The second cylinder is provided with a second intake pipe, one end of the second intake pipe is connected to the second intake chamber, and the other end is connected to a second liquid storage chamber via a second intake pipe. The first intake pipe and the second intake pipe are symmetrical about the centerline of the crankshaft. The first cylinder is provided with a first exhaust pipe, the two ends of which are in communication with the first exhaust chamber and the interior space of the housing, respectively. The second cylinder is provided with a second exhaust pipe, the two ends of which are in communication with the second exhaust chamber and the interior space of the housing, respectively. The first exhaust chamber and the second exhaust chamber are centrally symmetrical about the centerline of the crankshaft, and the first intake chamber and the second intake chamber are also centrally symmetrical about the centerline of the crankshaft. The second exhaust pipe and the first exhaust pipe are centrally symmetrical about the centerline of the crankshaft. The volumes of the first suction chamber and the second suction chamber are equal, and the volumes of the first exhaust chamber and the second exhaust chamber are equal; The shape of the radial cross-section of the first intake chamber along the crankshaft and the shape of the radial cross-section of the second intake chamber along the crankshaft are centrally symmetrical based on the center line of the crankshaft; the shape of the radial cross-section of the first exhaust chamber along the crankshaft and the shape of the radial cross-section of the second exhaust chamber along the crankshaft are centrally symmetrical based on the center line of the crankshaft.

2. The twin-cylinder compressor according to claim 1, characterized in that: The angle between the projection vector of the exhaust direction vector of the first exhaust pipe on a reference plane perpendicular to the central axis of the crankshaft and the projection vector of the exhaust direction vector of the second exhaust pipe on the reference plane is in the range of [5°, 180°].

3. The twin-cylinder compressor according to claim 1, characterized in that: The first liquid storage chamber is a first liquid reservoir, and the second liquid storage chamber is a second liquid reservoir.

4. The twin-cylinder compressor according to claim 3, characterized in that: The first liquid reservoir and the second liquid reservoir are sequentially arranged along the radial direction of the housing.

5. The twin-cylinder compressor according to claim 4, characterized in that: The first liquid reservoir and the second liquid reservoir are on the same side of the housing.

6. The twin-cylinder compressor according to claim 4, characterized in that: The first liquid reservoir and the second liquid reservoir are respectively located on both sides of the housing.

7. The twin-cylinder compressor according to claim 1, characterized in that: The first liquid storage chamber and the second liquid storage chamber are the same liquid reservoir.

8. The twin-cylinder compressor according to claim 1, characterized in that: The first liquid storage chamber and the second liquid storage chamber are respectively two separated independent inner chambers in a third liquid reservoir.

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