CN110645174B - Compressor and intermediate plate thereof - Google Patents
Compressor and intermediate plate thereof Download PDFInfo
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- CN110645174B CN110645174B CN201810672939.0A CN201810672939A CN110645174B CN 110645174 B CN110645174 B CN 110645174B CN 201810672939 A CN201810672939 A CN 201810672939A CN 110645174 B CN110645174 B CN 110645174B
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- piston
- reference line
- circle
- injection hole
- gas
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
- F04C18/30—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
- F04C18/34—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members
- F04C18/356—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member
- F04C18/3566—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member the inner and outer member being in contact along more than line or surface
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
- F04C23/001—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids of similar working principle
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
Abstract
The invention provides a compressor and an intermediate plate thereof, wherein the intermediate plate is provided with a gas injection hole which vertically penetrates through two end surfaces and is established in a perforable area defined by the intersection of three circles related to the outline of a piston, the perforable area is obtained by conversion according to the motion tracks of two pistons, and the cross section area of the gas injection hole is smaller than or equal to the area of the perforable area. Therefore, the two cylinders can be ensured not to be communicated with the blow-by gas through the gas orifice, and the gas orifice can not be communicated with the interior of the piston to absorb oil; in addition, the piston has a certain thickness, and can meet the requirement of opening and closing the gas orifice through the rotation of the piston; furthermore, the arrangement position of the air injection hole can ensure that air injection is started after most or all air suction of any air cylinder is finished, so that the influence of air injection on the air suction quantity is reduced; furthermore, the gas injection hole can be ensured to be closed before the exhaust pressure is increased until the exhaust valve plate is close to the opening pressure, so that the influence on the gas flow and the pressure loss caused by the gas flowing back to the gas injection pipe from the compression cavity is avoided.
Description
Technical Field
The invention relates to the technical field of compressors, in particular to a compressor and an intermediate plate thereof.
Background
The related art provides a rotary compressor with a gas injection function, which injects a part of refrigerant in a gaseous form into a cylinder through an injection system, and thus, not only can increase the cooling and heating capabilities of the compressor, particularly the heating capability under a low temperature condition, but also can improve the system capacity and efficiency of an air conditioning system, and thus, has been widely used.
In the existing double-cylinder enhanced vapor injection rotor compressor, an air injection hole is generally formed in a middle plate between two cylinders, and the communication between the air injection hole and a cylinder compression cavity is closed or conducted through the movement of a piston, so that the air injection hole is controlled to inject air into the two cylinders. However, two pistons generally are 180 degrees symmetry setting, make the position of fumarole on the intermediate deck need satisfy certain requirement, particularly, when one of them piston moves a certain position, the fumarole communicates with the compression chamber of cylinder, at this moment, at first, need ensure that the fumarole avoids the piston and not sheltered from by it, secondly, need guarantee that the pressure in the compression chamber this moment is less than jet-propelled pressure, just so can be through jet-propelled hole to the injection gas in the compression chamber, then when this piston moves next position, the pressure in the compression chamber increases to a certain extent, need utilize the piston to shelter from the fumarole this moment, cut off fumarole and compression chamber, consequently, static fumarole is in the in-process of piston motion, need be sheltered from by the piston sometimes, need avoid the piston sometimes, so the position of fumarole needs satisfy these requirements, can not set up at will. However, the problem that the conventional gas injection hole is opened simultaneously relative to the upper cylinder and the lower cylinder to cause blow-by between the upper cylinder and the lower cylinder or the gas injection hole is communicated with the inside of the piston in the process of piston movement to cause the gas injection hole to suck high-temperature and high-pressure refrigeration oil from the inside of the piston, and finally compression work loss and poor gas injection are caused cannot be solved well.
In addition, the larger the air injection amount is, the larger the improvement of the refrigerating capacity or the heating capacity of the compressor is, so that the cross-sectional area of the air injection hole is generally required to be increased as much as possible, thereby reducing the air injection resistance and improving the performance of the compressor. However, blindly enlarging the gas injection holes also causes the above-mentioned problems. In addition, blindly enlarging the gas injection holes can also cause the gas injection holes to open too early in the gas suction process of the cylinder, thereby affecting the gas suction flow and generating certain pressure loss, and in addition, can also cause the gas injection holes to close too late when the cylinder pressure exceeds the gas injection pressure, causing the gas in the compression cavity to flow back to the gas injection holes, thereby affecting the gas injection flow and generating pressure loss. Both of these conditions cause a loss of compression work, which in turn reduces the efficiency of the compressor.
Disclosure of Invention
The invention aims to provide a compressor and an intermediate plate thereof, which are used for solving one or more of the problems of air blow-by between cylinders, oil absorption of a gas injection hole and air leakage in the use process of a rotor compressor with a gas injection function.
In order to solve the technical problem, the present invention provides an intermediate plate of a compressor, configured to be disposed between two cylinders of the compressor, wherein the intermediate plate is provided with an air injection hole vertically penetrating two end surfaces, the air injection hole is established in a perforable region, a cross-sectional area of the air injection hole is smaller than or equal to an area of the perforable region, and the perforable region is defined by intersecting three circles, wherein:
the first circle is an orthographic projection of the outer contour of the piston in one cylinder on the end face of the middle plate, the second circle is an orthographic projection of the outer contour of the piston in the other cylinder on the same end face, the third circle is set on the same end face and has a preset radius, the center of the third circle is on the central axis of the middle plate, and the preset radius is the sum of the eccentric distance of any one piston and the inner radius of the piston; the intersection of the three circles has a first common portion, the intersection of the first circle and the second circle has a second common portion, and one of two complements of the first common portion in the second common portion serves as the holeable region.
Optionally, the cross-sectional area of the gas injection holes is not less than 20% of the area of the openable region.
Optionally, the gas injection hole is a special-shaped hole, or a round hole, or consists of a plurality of round holes arranged in parallel.
Optionally, when the gas injection hole is one circular hole, the circular hole is internally tangent to the first circle, the second circle and the third circle at the same time.
Optionally, when the gas injection hole is one of the profiled holes, the cross-sectional profile of the profiled hole is obtained by rounding the profile of the openable hole region.
Optionally, the calculation formula of the openable region is as follows:
wherein: e is the eccentricity of any one piston; r is the outer radius of any piston; r is the inner radius of any piston; alpha is an included angle between a first reference line and a second reference line, the first reference line is a central axis of an orthographic projection of a blade groove of any one cylinder on the same end face of the middle plate, the first reference line is intersected with the central axis of the middle plate, the second reference line is a connecting line of the orthographic projections of centers of two pistons on the same end face, and the second reference line is also intersected with the central axis of the middle plate; x is a coordinate value of any point in the openable region on an x axis of the rectangular coordinate system, and y is a coordinate value of any point in the openable region on a y axis of the rectangular coordinate system; the origin of rectangular coordinate system is on the central axis of intermediate lamella, the y axle with first reference line coincide and use the direction of pointing to the blade groove is the positive direction.
In addition, in order to solve the above technical problem, the present invention further provides a compressor, including at least two cylinders and the intermediate plate, wherein the intermediate plate is disposed between the at least two cylinders, and the air is injected into the at least two cylinders through the air injection holes on the intermediate plate, wherein:
a piston is arranged in any one of the cylinders, and the inner radius of the piston meets the following requirements:
r is the outer radius of any piston; e is the eccentricity of any one piston; r is the inner radius of any one piston.
Optionally, the compressor has a first reference line, the first reference line is a central axis of an orthographic projection of a blade groove of any one of the cylinders on the same end face of the intermediate plate, and the first reference line intersects with the central axis of the intermediate plate; wherein:
the orthographic projection of the air suction port of any one cylinder on the same end face and the air injection hole are positioned on different sides of the first reference line.
Optionally, the compressor further has a second reference line, the second reference line is a connection line of orthographic projections of centers of the two pistons on the same end face, the second reference line also intersects with the central axis of the middle plate, and an included angle between the first reference line and the second reference line is between-10 ° and +50 °.
Optionally, an included angle between the first reference line and the second reference line is-10 °, 0 °, or 50 °.
Compared with the prior art, the compressor and the intermediate plate thereof provided by the invention have the following beneficial effects:
the middle plate provided by the invention is provided with the gas orifice established in the open area, the cross section area of the gas orifice is smaller than or equal to the area of the open area, and the open area is defined by intersecting three circles, specifically, the cross section shape of the gas orifice is obtained by converting the motion tracks of two pistons, and the arrangement of the gas orifice can ensure that when the gas orifice is communicated with one cylinder of the compressor for gas injection, the gas orifice is completely closed (namely blocked by a piston) relative to the other cylinder, so that the problem of gas channeling between the two cylinders is avoided, and in the rotating process of the piston, the gas orifice can not be communicated with the inside of the piston all the time, so that the gas orifice can not suck high-temperature and high-pressure refrigeration oil from the inside of the piston, the loss of compression work is avoided, and the poor gas injection is overcome;
secondly, in the compressor provided by the invention, the inner diameter of the piston needs to satisfy the formula:
when the piston has a thickness (namely R-R) which meets the formula, the piston can meet the requirement of completely shielding the gas orifice in the rotating process, so that the gas orifice is opened and closed by the rotation of the piston;
thirdly, the compressor of the invention also has a first reference line, the first reference line is a central axis of an orthographic projection of the blade groove of any one cylinder on the same end surface of the middle plate, the first reference line is crossed with the central axis of the middle plate, and the orthographic projection of the air suction port of any one cylinder on the same end surface and the air injection hole are positioned on different sides of the first reference line, that is, the air injection holes on the middle plate need to be positioned at the other side of the air suction port of any cylinder, thus the air injection process and the air suction process of the cylinders can be separated, air injection is started after a part or all of air suction of one cylinder is finished, thereby reducing the influence of the air injection on the air suction flow, simultaneously ensuring that the air injection hole is closed before the exhaust pressure is increased to the exhaust valve plate to be close to the opening pressure, thereby avoiding the problems that the gas in the compression cavity flows back to the gas injection hole to influence the gas injection flow and generate pressure loss.
Drawings
The drawings are included to provide a better understanding of the invention and are not to be construed as unduly limiting the invention. Wherein:
fig. 1 is a schematic sectional view of a compressor according to a first embodiment of the present invention;
FIG. 2 is a schematic projection view of a first end surface of a middle plate according to a first embodiment of the present invention;
FIG. 3 is a schematic view showing the operation of the piston according to the first embodiment of the present invention;
FIG. 4 is a schematic perspective view of a middle plate according to a first embodiment of the present invention;
FIG. 5 is a schematic top view of a middle plate according to a first embodiment of the present invention;
FIG. 6 is a schematic top view of a compressor according to a first embodiment of the present invention;
FIG. 7 is a schematic cross-sectional view of a gas injection hole according to a second embodiment of the present invention;
FIG. 8 is a schematic top view of a compressor according to a second embodiment of the present invention;
FIG. 9 is a schematic cross-sectional view of a gas injection hole according to a third embodiment of the present invention;
fig. 10 is a schematic top view of a compressor according to a third embodiment of the present invention;
FIG. 11 is a schematic cross-sectional view of a gas injection hole according to a fourth embodiment of the present invention.
In the figure:
10-a middle plate; 11-gas injection holes; 100. 101-gas orifice profile; 110 — a second reference line; 111-third circle; 20-a first cylinder; 200-first end face center; 21-a first piston; 210 — first piston center; 211 — first piston outer circle; 22-a first vane slot; 220 — first reference line; 30-a second cylinder; 31-a second piston; 310-second piston center; 311-second piston outer circle; 32-a second vane slot; 40-air entry; 50-the central axis.
Detailed Description
The invention is described in further detail below with reference to the figures and specific examples. And the advantages and features of the present invention will be more apparent from the following description.
It is to be noted that the drawings are in a very simplified form and are not to precise scale, which is merely for the purpose of facilitating and distinctly claiming the embodiments of the present invention. Further, the structures illustrated in the drawings are often part of actual structures. In particular, the drawings may have different emphasis points and may sometimes be scaled differently.
As used in the claims and this specification, the singular forms "a," "an," and "the" include plural referents unless the content clearly dictates otherwise. As used in this specification, the term "or" is generally employed in its sense including "and/or" unless the content clearly dictates otherwise.
[ EXAMPLES one ]
Please refer to fig. 1, which is a schematic cross-sectional view of a compressor according to a first embodiment of the present invention, fig. 2 is a schematic projection view of a first end surface of an intermediate plate according to a first embodiment of the present invention, fig. 3 is a schematic view of a piston operation process according to a first embodiment of the present invention, fig. 4 is a schematic perspective view of the intermediate plate according to the first embodiment of the present invention, fig. 5 is a schematic top view of the intermediate plate according to the first embodiment of the present invention, and fig. 6 is a schematic top view of the compressor according to the first embodiment of the present invention.
As shown in fig. 1, an embodiment of the present invention provides a compressor, in particular, a two-cylinder rotary compressor, which includes an intermediate plate 10, a first cylinder 20, a first piston 21, a second cylinder 30, and a second piston 31. The first cylinder 20 is provided with the eccentric first piston 21, and the second cylinder 30 is provided with the eccentric second piston 31. Generally, the first cylinder 20 and the second cylinder 30 are the same size, and the first piston 21 and the second piston 31 are the same size. In addition, in the rotary compressor, the piston is generally ring-shaped, and the intermediate plate 10 is provided between the first cylinder 20 and the second cylinder 30 to partition the first cylinder 20 from the second cylinder 30, and further partition the first piston 21 from the second piston 31. In actual installation, the central axis of the middle plate 10 and the central axes of the first cylinder 20 and the second cylinder 30 are on the same central axis 50, that is, the three are coaxially disposed and stacked in parallel. Further, the middle plate 10 is provided with an air injection hole 11, and the air injection hole 11 vertically penetrates through two end surfaces (a first end surface and a second end surface, the first end surface is close to the first air cylinder 20, and the second end surface is close to the second air cylinder 30) of the middle plate 10, and is used for injecting air to one of the first air cylinder 20 and the second air cylinder 30.
Furthermore, in order to make the gas injection holes 11 not only be in communication with one cylinder but also not in communication with the interior of the piston during the movement of the piston, the present invention sets a perforated area on the intermediate plate 10, thereby creating the gas injection holes 11 in the perforated area, and the cross-sectional area of the gas injection holes 11 is smaller than or equal to the area of the perforated area. As shown in fig. 2, in the present invention, the openable region is defined by three circles intersecting, wherein:
the first circle is an orthographic projection 211 of the outer contour of the first piston 21 on the first end face of the intermediate plate 10, the second circle is an orthographic projection 311 of the outer contour of the second piston 31 on the first end face, the third circle 111 is set on the first end face and has a predetermined radius, the center of the third circle is on the central axis of the intermediate plate 10, and the predetermined radius is the sum (e + r) of the eccentricity of any one piston and the inner radius of the piston. R is the inner radius of any piston, i.e. the radius of the inner circle of the piston, e is the eccentricity of any piston, and e ═ R '-R, R' is the inner radius of the cylinder, R is the radius of the outer circle of any piston (i.e. the outer radius), i.e. the eccentricity e is the difference between the inner radius of the cylinder and the outer radius of the piston.
And the intersection of the three circles has a first common portion, the intersection of the first circle and the second circle has a second common portion of olive type, the two complements of the first common portion in the second common portion are two circular- sided triangles 100, 101 shaped like dovetails (shaded filled areas in the figure). One of the rounded triangles 100 is selected as the fenestratable region. Thus, in this open hole region, the gas injection holes 11 of arbitrary shape may be created, but the cross-sectional area of the gas injection holes 11 may be smaller than or equal to the area of the open hole region.
Next, the manner of acquiring the above-described openable region will be further described with reference to fig. 2. As shown in fig. 2, when the two pistons are in a stationary state, the center of the first piston 21 has an orthographic projection 210 on the first end surface, and the center of the second piston 31 also has an orthographic projection 310 on the first end surface, in practice, the two orthographic projections 210 and 310 are both a point, and a connecting line of the two points intersects with the central axis of the middle plate 10, that is, the two pistons are symmetrically arranged at 180 ° with respect to the central axis 50 of the middle plate 10. Here, the middle plate 10 has a first reference line 220 and a second reference line 110, the first reference line 220 is a central axis of an orthogonal projection of a vane groove of any one of the cylinders on the first end surface, the first reference line intersects the central axis of the middle plate 10, and a connection line between the two orthogonal projections 210 and 310 is defined as the second reference line 110 of the middle plate 10.
Further, in order to completely shield the gas ejection hole 11 during the rotation of the piston and open and close the gas ejection hole 11 by the rotation of the piston, any one of the pistons needs to satisfy the following requirements:
in the present invention, the second piston 31 has the same size as the first piston 21, and both of them satisfy the requirement.
Further, as shown in fig. 3, during the operation of the compressor, for example, from the state a → the state b → the state c, the state a is the state shown in fig. 2 where the two pistons rotate around the central axis 50 by 30 ° counterclockwise, the state b is the state where the two pistons rotate around the central axis 50 by 30 ° counterclockwise, and the state c is the state where the two pistons rotate around the central axis 50 by 30 ° counterclockwise, that is, in the state c, the two pistons rotate by 90 ° with respect to the state shown in fig. 2, obviously, the above states are repeated continuously when the pistons rotate further; during the entire rotation of the piston about the central axis 50, the two rounded triangles 100, 101 are at least covered by one piston during the rotation of the two pistons, and the inner circle of the piston does not enter the range of the two rounded triangles 100, 101. Obviously, the two rounded triangles 100 and 101 are used for defining the cross-sectional shape and position of the gas injection hole 11, so that the two cylinders cannot be communicated with the gas injection hole 11 at the same time, the gas injection hole 11 cannot be communicated with the inside of the piston, gas blowby between the two cylinders is avoided, and high-temperature and high-pressure refrigeration oil cannot be sucked from the inside of the piston by the gas injection hole.
The inventor finds that in the double-cylinder rotor compressor with the air injection function, the performance of the compressor is greatly influenced by the air blow-by between two cylinders and the suction of high-temperature and high-pressure refrigeration oil from the interior of a piston by an air injection hole, the two problems can cause the loss of compression work and poor air injection, and further the normal operation of the compressor is influenced, and the two problems can be better avoided by establishing the air injection hole 11 in the open hole area.
Referring next to fig. 4 and 5, a rounded triangle 100 located on the right side of the second reference line 110 may be used as the openable region, and in this embodiment, the rounded triangle 100 is the outline of the gas injection hole 11.
Referring to fig. 6, the first cylinder 20 has a first vane groove 22, and the first vane groove 22 is disposed perpendicular to the inner wall of the first cylinder 20, that is, the central axis of the first vane groove 22 intersects with the central axis of the first cylinder 20. The orthographic projection of the axis of the first vane slot 22 on the first end face is taken as a first reference line 220, and it is obvious that the first reference line 220 passes through the center 200 of the first end face, that is, intersects the central axis of the intermediate plate 10. In general, since the installation position of the second vane groove 32 in the second cylinder 30 is the same as the installation position of the first vane groove 22 in the first cylinder 20, orthographic projections of the central axes of the first vane groove 22 and the second vane groove 32 on the first end surface are both the first reference line 220.
In the present embodiment, the first cylinder 20 further has a first intake port, and an orthographic projection of the first intake port on the first end surface is located on a first side of the first reference line 220, where the second cylinder 30 has a second intake port, and in general, orthographic projections of the intake ports of the two cylinders on the first end surface are located at the same position. Further, the perforated region 100 is located on a second side (shown as the right side) of the first reference line 220. Here, the gas injection hole 11 and the gas suction port are disposed on different sides of the first reference line 220, so that a gas injection process of the gas injection hole and a gas suction process of the cylinder can be separated, and the influence of the gas injection on the gas suction process can be reduced.
In one non-limiting operator: a rectangular coordinate system is established on the middle plate 10, the origin of the rectangular coordinate system is set at the center 200 of the first end surface, the y-axis coincides with the first reference line 220, the direction of the first reference line 220 pointing to the vane slot is the forward direction of the y-axis, the x-axis is along the radial direction of the first end surface and the second side facing the first reference line 220 is the forward direction, wherein the second reference line 110 and the y-axis are set to form a predetermined included angle α, that is, the first reference line 220 and the second reference line 110 are set to form the predetermined included angle, and the predetermined included angle is preferably in the range of-10 ° to +50 °.
Further, the inventor finds that when the range of the preset included angle alpha is-10 degrees to +50 degrees, the air injection hole can be opened only after most or all of air suction of one air cylinder is finished in the rotating process of the piston, so that the influence of air injection on the air suction quantity is reduced; in addition, the predetermined included angle α is set to ensure that the gas injection hole is closed before the discharge pressure is increased until the discharge valve plate approaches the opening pressure, so as to avoid influencing the gas injection flow and generating pressure loss due to the backflow of the gas in the compression chamber to the gas injection hole, and particularly, the angle α is set to be 0 degree when the second reference line 110 is in positive coincidence with the y axis, and α is negative when the second reference line 110 is located in the first quadrant and the third quadrant of the rectangular coordinate system, and is positive when the second reference line 110 is located in the second quadrant and the fourth quadrant.
Preferably, the predetermined included angle α is 50 °, that is, the second reference line 110 is located in the second and fourth quadrants of the coordinate system, and the inventor finds that, when α is 50 °, the gas injection hole can be opened only after the gas suction of one cylinder is completed, and the gas injection hole can also be ensured to be closed before the exhaust pressure is increased to the exhaust valve plate approaches the opening pressure; therefore, air leakage of the jet gas in the processes of air suction and air exhaust is effectively avoided, pressure loss is avoided, and the efficiency of the compressor is effectively improved.
In the embodiment of the present invention, the calculation formula of the openable region is as follows:
wherein: e is the eccentricity of any one piston; r is the outer radius of any piston; r is the inner radius of any piston; alpha is the included angle between the first reference line and the second reference line; and x is a coordinate value of any point in the openable region on the x axis of the rectangular coordinate system, and y is a coordinate value of any point in the openable region on the y axis of the rectangular coordinate system.
[ example two ]
Referring to fig. 7 and 8, fig. 7 is a schematic cross-sectional view of a gas injection hole according to a second embodiment of the present invention, and fig. 8 is a schematic top view of a compressor according to the second embodiment of the present invention;
referring to fig. 7, the difference from the first embodiment is: the gas injection hole profile of the present embodiment is different from that of the first embodiment in that, as described in the first embodiment, three circles intersect to have two complements of a first common portion in an olive-shaped second common portion where the first circle and the second circle intersect, i.e., circular triangles 100, 101 shaped like a dovetail, and one of the circular triangles 100 located at the right side of the second reference line 110 is taken as the openable region, and the circular triangle 100 is also taken as the gas injection hole 11, so that the gas injection hole 11 has the largest open area. Then, in this embodiment, the gas orifice 11 is obtained by rounding the outline of the rounded triangle 100, specifically, the rounded triangle 100 has three vertexes a, b, and c, the radius of one of the arcs is the radius r3 of the third circle 111, 1/5 of r3 is taken as the radius, and the three vertexes a, b, and c are rounded respectively to obtain a special-shaped area, which is taken as the cross section of the gas orifice of this embodiment. Here, the rounding specifically means: taking any two arc-shaped edges, taking 1/5 of the r3 as a radius to form an arc which is tangent to and protrudes outwards from the two arc-shaped edges, and sequentially connecting the arc-shaped edges and the protruding arc end to end.
The inventor finds that when the area of the special-shaped area is not less than 20% of the area of the round-edge triangle 100, the air injection amount of the air injection hole can effectively improve the refrigerating capacity or the heating capacity of the compressor.
The inventor further found that although the outline of the gas injection hole 11 may be formed by the rounded triangle 100 as described in the first embodiment, the vertices a and b of the rounded triangle 100 are acute angles, and it is not easy to produce if a milling process is used, so that a deformed area not less than 20% of the area of the rounded triangle 100 is created as the cross section of the gas injection hole 11, which can facilitate production and achieve a better gas injection effect.
Therefore, the radius of the rounded corner is not limited to 1/5 of r3 as the radius, and the area of the deformed region generated in a similar way is not less than 20% of the area of the rounded triangle 100, which is within the protection scope of the invention.
Referring to fig. 8, the difference between the present embodiment and the first embodiment is further: the predetermined included angle α formed by the second reference line 110 and the Y axis is 0 °, that is, the second reference line 110 coincides with the first reference line 220; at this time, the gas ejection hole is located in the positive direction of the X-axis. The inventor finds that when the gas injection hole 11 is located at this position, in the process of piston rotation, the gas injection hole can be opened only after one cylinder basically finishes gas suction, compared with the first embodiment, although the gas injection hole is not opened until the gas suction is finished completely, the influence of gas injection on the gas suction amount is very small; when the air injection hole is located at the position, compared with the first embodiment, the air injection hole is opened and closed earlier, the air injection pressure can be obviously reduced, the air injection effect is obviously improved, and the efficiency of the compressor is further improved greatly.
[ EXAMPLE III ]
Referring to fig. 9 and 10, fig. 9 is a schematic cross-sectional view of a gas injection hole according to a third embodiment of the present invention, and fig. 10 is a schematic top view of a compressor according to a third embodiment of the present invention;
referring to fig. 9, the difference from the first embodiment is: the gas orifice 11 comprises a plurality of round holes that are arranged side by side, and is specific in the round triangle 100, take a plurality of continuous round holes as the cross section of the gas orifice 11 of this embodiment, for example, comprise five round holes that intersect in proper order, five round holes all with at least two in the three arc sides of round triangle 100 are tangent. In addition, the cross section area of the gas injection hole 11 formed by connecting a plurality of circular holes is not less than 20% of the area of the round-edged triangle 100, and the shape is convenient for production and can obtain better gas injection effect. Similarly, the number of the above-mentioned connected circular holes is not limited to five, nor to being tangent to the arc-shaped side of the rounded triangle 100, and the area of the connected circular holes generated in a similar manner is not less than 20% of the area of the rounded triangle 100, which is within the protection scope of the present invention.
Referring to fig. 10, the difference between the present embodiment and the first embodiment is further: the predetermined included angle α formed by the second reference line 110 and the Y-axis is-10 °, that is, the second reference line 110 is located in one quadrant and three quadrants of the coordinate system; at this time, the gas injection hole is partially or entirely located in the fourth quadrant of the coordinate system. The inventor finds that when the air injection hole is at the position, the air injection hole can be opened only after air suction of one air cylinder is basically finished in the rotating process of the piston, and compared with the second embodiment, the influence of air injection on the air suction quantity is slightly larger; and when the air injection hole is located at this position, compared with the second embodiment, the air injection hole is opened and closed earlier, so that the air injection pressure can be reduced more obviously, and the air injection effect is improved more obviously.
The inventor further finds that in the present embodiment, although early injection may slightly affect the suction flow and may generate a certain pressure loss, in the double-cylinder rotor compressor, the impact is not as great as that of the single-cylinder rotor compressor, and on the other hand, reducing the injection pressure can significantly improve the injection effect, thereby significantly improving the efficiency of the compressor, so that the injection hole can also achieve a better effect at this position.
[ EXAMPLE IV ]
Please refer to fig. 11, which is a schematic cross-sectional view of a gas injection hole according to a fourth embodiment of the present invention, the difference between the first embodiment and the second embodiment is: in the round-edged triangle 100, a round hole tangent to three arc-shaped edges of the round-edged triangle 100 is taken as the cross section of the gas orifice 11 in the embodiment, and the area of the round hole is not less than 20% of the area of the round-edged triangle 100, so that the production is also convenient, and a better gas injection effect can be obtained.
It should be noted that, the cross-sectional shape of the gas injection hole in the above embodiments may be selected from other shapes as long as the area of the gas injection hole is ensured to be not less than 20% of the area of the rounded triangle 100, which is not limited in the present invention.
The above description is only for the purpose of describing the preferred embodiments of the present invention, and is not intended to limit the scope of the present invention, and any variations and modifications made by those skilled in the art based on the above disclosure are within the scope of the appended claims.
Claims (10)
1. An intermediate plate of a compressor for being disposed between two cylinders of the compressor, wherein the intermediate plate is provided with a gas injection hole that vertically penetrates both end surfaces, the gas injection hole being established in a perforable region whose cross-sectional area is smaller than or equal to an area of the perforable region defined by intersection of three circles, wherein:
the first circle is an orthographic projection of the outer contour of the piston in one cylinder on the end face of the middle plate, the second circle is an orthographic projection of the outer contour of the piston in the other cylinder on the same end face, a connecting line of the circle center of the first circle and the circle center of the second circle is intersected with the central axis of the middle plate, and the first circle and the second circle are symmetrically arranged in an angle of 180 degrees relative to the central axis of the middle plate; a third circle is set on the same end face and has a preset radius, the center of the third circle is on the central axis of the middle plate, and the preset radius is the sum of the eccentricity of any one piston and the inner radius of the piston; the intersection of the three circles has a first common portion, the intersection of the first circle and the second circle has a second common portion, and one of two complements of the first common portion in the second common portion serves as the holeable region.
2. The intermediate plate of a compressor according to claim 1, wherein a cross-sectional area of the gas injection hole is not less than 20% of an area of the openable region.
3. The middle plate of a compressor according to claim 2, wherein the gas injection hole is a shaped hole, or a circular hole, or is composed of a plurality of circular holes arranged in parallel.
4. The middle plate of a compressor according to claim 3, wherein when the gas injection hole is one of the circular holes, the circular hole is simultaneously inscribed in the first circle, the second circle, and the third circle.
5. The intermediate plate of a compressor according to claim 3, wherein when the gas injection hole is one of the shaped holes, a cross-sectional profile of the shaped hole is rounded from a profile of the holeable region.
6. The intermediate plate of a compressor according to claim 1 or 2, wherein the calculation formula of the openable region is:
wherein: e is the eccentricity of any one piston; r is the outer radius of any piston; r is the inner radius of any piston; alpha is an included angle between a first reference line and a second reference line, the first reference line is a central axis of an orthographic projection of a blade groove of any one cylinder on the same end face of the middle plate, the first reference line is intersected with the central axis of the middle plate, the second reference line is a connecting line of the orthographic projections of centers of two pistons on the same end face, and the second reference line is also intersected with the central axis of the middle plate; x is a coordinate value of any point in the openable region on an x axis of the rectangular coordinate system, and y is a coordinate value of any point in the openable region on a y axis of the rectangular coordinate system; the origin of rectangular coordinate system is on the central axis of intermediate lamella, the y axle with first reference line coincide and use the direction of pointing to the blade groove is the positive direction.
7. A compressor comprising at least two cylinders, further comprising an intermediate plate according to any one of claims 1 to 6, and at least two of the cylinders are interposed therebetween and gas is injected into at least two of the cylinders through the gas injection holes in the intermediate plate, wherein:
a piston is arranged in any one cylinder, and the inner radius of the piston meets the following requirements:
r is the outer radius of any piston; e is the eccentricity of any one piston; r is the inner radius of any one piston.
8. The compressor according to claim 7, wherein the compressor has a first reference line, the first reference line being a central axis of an orthographic projection of a vane groove of any one of the cylinders on the same one of the end faces of the intermediate plate, the first reference line intersecting the central axis of the intermediate plate; wherein:
the orthographic projection of the air suction port of any one cylinder on the same end face and the air injection hole are positioned on different sides of the first reference line.
9. The compressor according to claim 8, wherein the compressor further has a second reference line, the second reference line is a connection line of orthographic projections of centers of the two pistons on the same end surface, the second reference line also intersects with the central axis of the intermediate plate, and the first reference line and the second reference line form an angle between-10 ° and +50 °.
10. The compressor of claim 8, wherein the first reference line is angled at-10 °, 0 °, or 50 ° from the second reference line.
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| CN201810672939.0A CN110645174B (en) | 2018-06-26 | 2018-06-26 | Compressor and intermediate plate thereof |
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| CN201810672939.0A CN110645174B (en) | 2018-06-26 | 2018-06-26 | Compressor and intermediate plate thereof |
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| JPH1113664A (en) * | 1997-06-27 | 1999-01-19 | Daikin Ind Ltd | Rotary compressor |
| CN1226640A (en) * | 1998-02-13 | 1999-08-25 | 松下电器产业株式会社 | Hermetic compressor |
| CN101294568A (en) * | 2007-04-25 | 2008-10-29 | 珠海格力电器股份有限公司 | Rotary compressor with air injection enthalpy-increasing function |
| JP2012057568A (en) * | 2010-09-10 | 2012-03-22 | Panasonic Corp | Rotary compressor and refrigeration cycle device |
| CN106224239A (en) * | 2016-09-26 | 2016-12-14 | 广东美芝精密制造有限公司 | Pump assembly and the compressor assembly with it |
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2018
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Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH1113664A (en) * | 1997-06-27 | 1999-01-19 | Daikin Ind Ltd | Rotary compressor |
| CN1226640A (en) * | 1998-02-13 | 1999-08-25 | 松下电器产业株式会社 | Hermetic compressor |
| CN101294568A (en) * | 2007-04-25 | 2008-10-29 | 珠海格力电器股份有限公司 | Rotary compressor with air injection enthalpy-increasing function |
| JP2012057568A (en) * | 2010-09-10 | 2012-03-22 | Panasonic Corp | Rotary compressor and refrigeration cycle device |
| CN106224239A (en) * | 2016-09-26 | 2016-12-14 | 广东美芝精密制造有限公司 | Pump assembly and the compressor assembly with it |
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| CN110645174A (en) | 2020-01-03 |
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