Patent Description:
Taking a rotary cylinder compressor as an example, it is a new type of volumetric compressor. Its cylinder and rotation shaft rotate around their respective centers, and the piston reciprocates with respect to the cylinder and the rotation shaft at the same time. The reciprocating motion of the piston with respect to the cylinder enables periodical enlarging and reducing of the volume cavity; the circular motion with respect to the cylinder sleeve enables communication of the volume cavity with the intake passage and the exhaust passage, respectively. The above two motions cooperate to enable the intake, compression and exhaust processes of the compressor.

With the higher and higher requirement of high efficiency and energy saving for compressors, it is necessary to optimize the design of the rotary cylinder compressor to further improve efficiency of the compressor and achieve energy saving and emission reduction. Currently, during running of a rotary cylinder compressor, the rotation shaft divides the sliding hole in the piston into two cavities, and when the rotation shaft of the pump body assembly is sliding with respect to the piston, the two cavities of the sliding hole increase and decrease periodically. and the inner wall of the sliding hole of the piston presses the oil liquid in the sliding hole such that the oil liquid is transferred within the two cavities to achieve the oil pressing process. However, during practical running of a compressor, when the inner wall of the sliding hole of the piston presses the oil liquid, the fluency of the oil liquid will be impeded. During the oil pressing process, the oil liquid causes increase in power consumption of the piston and the rotation shaft, resulting in an increase in power consumption of the pump body assembly of the rotary cylinder compressor.

As can be seen from above, currently, there is a problem that the piston impedes a flow of oil liquid during use of rotary cylinder compressors.

Patent application document No. <CIT> discloses a rotary cylinder piston compressor pump and a compressor including the compressor pump. The compressor pump includes a rotating shaft, a piston and a cylinder. A rotating shaft hole is provided in the rotating shaft. An oil guiding channel communicated with the rotating shaft hole is provided in the cylinder. A recess is formed in the inner end face of the cylinder. An oil path sealed relative to a compression cavity of the cylinder is formed between the recess and the piston. The oil path is communicated with an oil path between the piston and the rotating shaft and is communicated with the oil guiding channel by means of an oil returning channel.

Patent application document No. <CIT> discloses a pump body assembly, a fluid machine and heat exchange equipment. The pump body assembly includes an air cylinder sleeve, an air cylinder and a piston, the air cylinder is rotationally arranged in the air cylinder sleeve, and the piston is slidably arranged in the air cylinder; the pump body assembly further includes a rotary shaft including a cooperation section, the cooperation section is arranged in the piston in a penetrating mode to drive the piston to move, the outer surface of the cooperation section is provided with two first cooperation planes that are horizontally arranged, and the first cooperation planes make contact with the piston, so that the rotary shaft can drive the piston to move; and the rotary shaft is provided with an axial oil passing hole, the first cooperation planes are provided with first oil grooves, the first oil grooves are communicated with the axial oil passing hole, and the extending direction of the first oil groove is perpendicular to the extending direction of the rotary shaft.

Patent application document No. <CIT> discloses a pump body structure of a rotary cylinder piston compressor, the rotary cylinder piston compressor and a pump body assembly of the rotary cylinder piston compressor. The pump body structure includes a rotating shaft including a shaft body and a shaft inner hole arranged in the shaft body; a piston; and at least one shaft oil groove. The shaft inner hole extends along the axial direction of the shaft body; the shaft body is provided with a shaft matching part matched with a piston, the peripheral wall of the shaft matching part is provided with two first planes that are oppositely arranged, and the rotating shaft reciprocates relative to the piston in the direction parallel to the first planes; and at least one shaft oil hole is formed between the hole wall of the shaft inner hole and the first plane in a penetrating mode. The piston is provided with a rotating shaft mounting hole allowing the rotating shaft to penetrate through, the hole wall of the rotating shaft mounting hole is provided with two second planes that are oppositely arranged, and the second plane is matched with the first plane on the corresponding side. The at least one shaft oil groove is formed on the at least one first plane and extends in the axial direction of the shaft body, and the shaft oil groove is communicated with the shaft oil hole.

Patent application document No. <CIT> discloses a pump body of a rotary cylinder piston compressor and a compressor adopting the pump body. The pump body includes a rotary shaft, a piston and an air cylinder, a rotary shaft hole is disposed in the rotary shaft; an oil guiding channel communicated with the rotary shaft hole is disposed in the air cylinder; and the crossed area of the rotary shaft hole and the oil guiding channel is greater than <NUM>% of the cross-section area of the rotary shaft hole.

Patent application document No. CN<CIT> discloses an air cylinder of a rotary cylinder piston compressor, a pump body assembly and the rotary cylinder piston compressor. The air cylinder of the rotary cylinder piston compressor includes a cylinder body, a piston mounting hole being formed in the peripheral wall of the cylinder body in a penetrating mode; and at least one oil guiding hole extending from the hole wall of the piston mounting hole to the outer peripheral surface of the cylinder. The at least one oil guiding hole is formed in the cylinder body, so that oil in the piston mounting hole can flow to the outer peripheral surface of the air cylinder through the oil guiding hole, thus lubricating between the air cylinder and the air cylinder sleeve.

The main purpose of the present disclosure is to provide a pump body assembly and a fluid machine to solve the problem in prior art that the piston impedes a flow of oil liquid during use of rotary cylinder compressors.

In order to achieve the above purpose, according to an aspect of the present disclosure, a pump body assembly is provided, comprising a rotation shaft and a piston provided with a sliding hole, at least a portion of the rotation shaft penetrates into the sliding hole, so as to divide a portion inside the piston into two cavities, during rotation of the piston with the rotation shaft, the two cavities increase and decrease periodically, and the sliding hole is in sliding fit with the rotation shaft, so that oil liquid is pressed at an inner wall of the sliding hole, and the piston is provided with a piston communication passage communicated with the sliding hole, so as to fluently transfer the oil liquid between the two cavities;.

In some embodiments, a plurality of the piston communication passages are provided.

In some embodiments, the number of the piston communication passages is less than <NUM>.

In some embodiments, on the end face of the same end of the piston, a group of two opposite edges of the sliding hole is respectively provided with at least one piston communication groove(s).

In some embodiments, in the axial direction of the rotation shaft, the piston is provided, at its top end face and its bottom end face, with the piston communication groove.

In some embodiments, with the piston communication groove as a boundary, the end face on a side where the piston communication groove is located comprises a first surface P1 and a second surface P2, wherein the first surface P1 is in a region between the piston communication groove and an edge of the sliding hole on the side where the piston communication groove is located, and the second surface P2 is in a region between the piston communication groove and an outer edge of the piston.

In some embodiments, the flexible groove is located at an end of the piston communication groove.

In some embodiments, a plurality of the flexible grooves are provided, and both ends of the same piston communication groove are respectively provided with one flexible groove such that a sliding boss protruding from the hole wall face of the sliding hole is formed within the sliding hole.

In some embodiments, ends of the flexible groove penetrate through the end faces on both ends of the piston along the axial direction of the rotation shaft.

In some embodiments, the flexible groove comprises a first groove surface and a second groove surface which are connected in sequence in a direction close to a middle portion of the sliding hole; a first transition fillet ∠<NUM> is formed between the first groove surface and the hole wall face of the sliding hole, a second transition fillet ∠<NUM> is formed between the second groove surface and the first groove surface, and a third transition fillet ∠<NUM> is formed at an edge on a side of the second groove surface far away from first groove surface.

In some embodiments, the pump body assembly further comprises a cylinder sleeve and a cylinder, wherein the cylinder is rotatably arranged in the cylinder sleeve and the cylinder is provided thereon, in its radial direction, with a piston hole, the piston is slidably arranged in the piston hole, the rotation shaft penetrates through the piston and drives the piston to reciprocate in an extension direction of the piston hole, and the cylinder rotates to cause rotation of the piston.

According to another aspect of the present disclosure, a fluid machine is provided, comprising the pump body assembly.

With the technical solutions of the present disclosure, the pump body assembly comprises a rotation shaft and a piston provided with a sliding hole, with at least a portion of the rotation shaft penetrating into the sliding hole, during rotation of the piston with the rotation shaft, the sliding hole is in sliding fit with the rotation shaft, wherein the piston is provided with a piston communication passage communicated with the sliding hole.

As can be seen from the above description, in the above embodiment(s) of the present disclosure, by setting the piston communication passage in the sliding hole of the piston, the fluency of oil liquid flow is increased and the power consumption of the pump body assembly is reduced. Currently, during running of a rotary cylinder compressor, when the rotation shaft of the pump body assembly is sliding with respect to the piston, an inner wall of the sliding hole of the piston will impede fluency of oil liquid flow when pressing the oil liquid and cause increase in power consumption of the pump body assembly.

Specifically, the rotation shaft penetrates through the sliding hole on the piston and divides the portion inside the piston into two cavities. During movement of the pump body assembly, the piston reciprocates with respect to the rotation shaft, and the two cavities increase and decrease periodically to achieve the oil pressing process. During the reciprocating movement of the piston, the inner wall of the sliding hole of the piston will press the oil liquid to enable transfer of the oil liquid between the two cavities. The piston communication passage communicated with the sliding hole is disposed on the piston so as to improve fluency of oil liquid transfer, to decrease resistance to pressing oil liquid by the piston, to reduce power consumption of the rotation shaft and the piston during the oil pressing process, and to reduce power consumption of the pump body assembly.

The accompanying drawings for the description, which constitutes a portion of the present application, are used to provide further understanding to the present disclosure. The illustrative embodiments of the present disclosure and the description thereof are used to explain the present disclosure, rather than forming inappropriate limitation to the present disclosure. In the drawings/figures:.

Herein, the above figures comprise the following reference numerals:.

<NUM> cylinder; <NUM> piston hole; <NUM> stop convex ring; <NUM> avoidance recess; <NUM> first face segment; <NUM> second face segment; <NUM> piston; <NUM> sliding hole; <NUM> piston communication groove; <NUM> sliding boss; <NUM> flexible groove; <NUM> sliding face; <NUM> rotation shaft; <NUM> sliding fit face; <NUM> rotation shaft flow-through hole; <NUM> rotation shaft communication groove; <NUM> long shaft segment; <NUM> short shaft segment; <NUM> connection face; <NUM> cylinder sleeve; <NUM> volume cavity; <NUM> lower flange; <NUM> positioning boss; <NUM> avoidance recess; <NUM> flange hole; <NUM> first segment; <NUM> second segment; <NUM> support rib.

It should be noted that the embodiments in the present application and the features therein can be combined with one another if there is no contradiction. Hereinafter, the present disclosure will be explained in detail with reference to the accompanying drawings and in combination with the embodiments.

It should be pointed out that any technical or scientific term used in the present application has the same meaning as generally understood by those skilled in the art of the present application, unless otherwise specified.

In the present disclosure, the used direction-position expressions, such as "above", "below", "top", "bottom", are generally used with respect to the direction(s) as shown in the figures, or with respect to the vertical, perpendicular or gravity direction for a part per se, unless specified on the contrary. Similarly, in order to facilitate understanding and description, the expressions of "inner" and "outer" refer to inner and outer portions of contours of parts per se. However, the above direction-position expressions are not used to limit the present disclosure.

In order to solve the problem in prior art that oil liquid flow is impeded during use of rotary cylinder compressors due to structures of a cylinder <NUM>, a piston <NUM>, a rotation shaft <NUM> and a flange, a pump body assembly and a fluid machine are provided in the present application.

Herein, the fluid machine comprises the pump body assembly as described below. Specifically, the fluid machine is a compressor. In some embodiments, the compressor is a rotary cylinder compressor.

In order to solve the problem in prior art of impediment to oil liquid flow during use of rotary cylinder compressors, it is possible to optimize the piston <NUM> so as to reduce impediment of the piston <NUM> to the oil liquid, thereby reducing power consumption of the pump body assembly.

Specifically, as shown in <FIG>, a pump body assembly comprises a rotation shaft <NUM> and a piston <NUM> provided with a sliding hole <NUM>, at least a portion of the rotation shaft <NUM> penetrates into the sliding hole <NUM>, wherein during rotation of the piston <NUM> with the rotation shaft <NUM>, the sliding hole <NUM> is in sliding fit with the rotation shaft <NUM>. The piston <NUM> is provided with a piston communication passage communicated with the sliding hole <NUM>.

As can be seen from the above description, in the above embodiment of the present disclosure, a piston communication passage is provided inside the sliding hole <NUM> of the piston <NUM> so as to improve fluency of oil liquid flow and reduce power consumption of the pump body assembly. Currently, during running of a rotary cylinder compressor, when the rotation shaft <NUM> of the pump body assembly is sliding with respect to the piston <NUM>, an inner wall of the sliding hole <NUM> of the piston <NUM> will impede fluency of oil liquid flow when pressing the oil liquid and cause increase in power consumption of the pump body assembly.

Specifically, the rotation shaft <NUM> penetrates into the sliding hole <NUM> on the piston <NUM> and divides the portion inside the piston <NUM> into two cavities. During movement of the pump body assembly, the piston <NUM> reciprocates with respect to the rotation shaft <NUM>, and the two cavities increase and decrease periodically to achieve the oil pressing process. During the reciprocating movement of the piston <NUM>, the inner wall of the sliding hole <NUM> of the piston <NUM> will press the oil liquid to enable transfer of the oil liquid between the two cavities. The piston communication passage communicated with the sliding hole <NUM> is disposed on the piston <NUM> so as to improve fluency of oil liquid transfer, to decrease resistance to pressing oil liquid by the piston <NUM>, to reduce power consumption of the rotation shaft <NUM> and the piston <NUM> during the oil pressing process, and to reduce power consumption of the pump body assembly.

In some embodiments, the number of the piston communication passages is less than <NUM>. If the number of the piston communication passages is more than <NUM>, the strength of the piston <NUM> will be affected, which will lead to insufficient stability of the piston <NUM> and decreased oil pressing power, and thus affect the whole running efficiency of the pump body assembly.

It should be noted that in the specific embodiments as shown in <FIG>, there are various implementations according to the difference(s) in the position(s) provided for the piston communication passage(s) and the shape(s) of the piston communication passage(s) as long as the impediment to oil liquid during the oil pressing process due to the piston <NUM> can be reduced, and they will not be described herein one by one.

Hereinafter, according to different structures for the piston communication passages disposed on the piston <NUM>, various implementations in <FIG> are provided.

In a specific implementation as shown in <FIG>, a piston communication passage is disposed on a hole wall face of the sliding hole <NUM>. The piston communication passage is a rectangular piston communication groove <NUM> having a uniform depth from place to place.

Specifically, by setting a rectangular piston communication groove <NUM> on the hole wall face of the sliding hole <NUM> of the piston <NUM>, the piston communication groove <NUM> extends in the sliding direction of the piston <NUM> and constitutes the piston communication passage, thus enlarging the flow path of the oil liquid. When the hole wall face of the sliding hole <NUM> of the piston <NUM> presses the oil liquid, the oil liquid can be transferred via the piston communication groove <NUM>, improving fluency of oil liquid transfer and also reducing power consumption of the piston <NUM> and the rotation shaft <NUM> during the oil pressing process.

In a specific implementation as shown in <FIG>, a piston communication passage is disposed on a hole wall face of the sliding hole <NUM>. The piston communication passage is a piston communication grooves <NUM> in a crescent shape.

It should be noted that in the sliding direction of the piston <NUM>, the piston communication groove <NUM> has a depth H2 gradually increasing from both ends of the piston communication groove <NUM> towards a middle portion of the piston communication groove <NUM>, thus forming the piston communication groove <NUM> in a crescent shape.

Specifically, by setting a piston communication groove <NUM> in a crescent shape on the hole wall face of the sliding hole <NUM> of the piston <NUM>, the piston communication groove <NUM> extends in the sliding direction of the piston <NUM> and constitutes the piston communication passage, thus enlarging the flow path of the oil liquid. When the hole wall face of the sliding hole <NUM> of the piston <NUM> presses the oil liquid, the oil liquid can be transferred via the piston communication groove <NUM>, improving fluency of oil liquid transfer and also reducing power consumption of the piston <NUM> and the rotation shaft <NUM> during the oil pressing process.

In specific implementations as shown in <FIG>, a plurality of the piston communication passages are provided, the plurality of the piston communication passages are disposed on an end face of the piston <NUM> in an axial direction of the rotation shaft <NUM>. The piston communication passage is the piston communication groove <NUM>.

In some embodiments, the piston communication groove <NUM> extends in a sliding direction of the piston <NUM> and constitutes the piston communication passage.

Specifically, by setting the piston communication passage on an end face of the piston <NUM> in an axial direction of the rotation shaft <NUM>, the flow path of the oil liquid is enlarged. When the hole wall face of the sliding hole <NUM> of the piston <NUM> presses the oil liquid, the oil liquid can be transferred via the piston communication groove <NUM>, improving fluency of oil liquid transfer and also reducing power consumption of the piston <NUM> and the rotation shaft <NUM> during the oil pressing process.

As shown in <FIG>, on the end face of the same end of the piston <NUM>, a group of two opposite edges of the sliding hole <NUM> is respectively provided with at least one piston communication groove <NUM>. By setting the piston communication groove <NUM> at the two edges in opposite positions of the sliding hole <NUM>, when the piston <NUM> presses the oil liquid, the oil liquid can be transferred via the piston communication groove <NUM>, improving movement fluency of oil liquid and reducing power consumption of the pump body assembly.

As shown in <FIG>, in the axial direction of the rotation shaft <NUM>, the piston <NUM> is provided, at each of its top end face and its bottom end face, with the piston communication groove <NUM>. The piston communication groove <NUM> is disposed at each of the top end face and the bottom end face of the piston <NUM>, to enlarge the flow path of the oil liquid. When the inner wall of the sliding hole <NUM> of the piston <NUM> presses the oil liquid, the movement fluency of oil liquid is improved and the power consumption of the pump body assembly is reduced.

As shown in <FIG>, with the piston communication groove <NUM> as a boundary, the end face on a side where the piston communication groove <NUM> is located comprises a first surface P1 and a second surface P2, wherein the first surface P1 is in a region between the piston communication groove <NUM> and an edge of the sliding hole <NUM> on a side where the piston communication groove <NUM> is located, and the second surface P2 is in a region between the piston communication groove <NUM> and an outer edge of the piston <NUM>. Thus, during movement of the piston <NUM>, the second surface P2 will not contact the cylinder, thereby preventing friction.

Specifically, a difference in height between the first surface P1 and the second surface P2 is <NUM>. When the difference in height is greater than <NUM>, it is possible to affect the strength of the piston <NUM> due to the difference in height being too large. When difference in height is less than <NUM>, the flowability of oil liquid cannot be effectively improved and the power consumption of the pump body assembly during the oil pressing process cannot be reduced.

As shown in <FIG>, a distance L2 between the piston communication groove <NUM> and an outer edge of the end face of the piston <NUM> on a side where the piston communication groove <NUM> is located is greater than or equal to <NUM>. When the distance between the piston communication groove <NUM> and an outer edge of the end face of the piston <NUM> on a side where the piston communication groove <NUM> is located is less than <NUM>, the strength of the piston <NUM> will be affected due to the wall thickness of the piston <NUM> being too small, the piston <NUM> is prone to be damaged during running such that the pump body assembly can not operate normally.

In specific implementations as shown in <FIG>, a plurality of the piston communication passages are provided, the plurality of the piston communication passages are disposed on an end face of the piston <NUM> in an axial direction of the rotation shaft <NUM>. The piston communication passage is a combined structure of the piston communication groove <NUM> and the flexible groove <NUM>, wherein the flexible groove <NUM> is disposed within the sliding hole <NUM> of the piston <NUM> and is located at an end of the piston communication groove <NUM>.

In some embodiments, the flexible groove <NUM> extends in the axial direction of the rotation shaft <NUM>, and the flexible groove <NUM> is communicated at its end with the piston communication groove <NUM>.

Specifically, by setting the piston communication groove <NUM> and the flexible groove <NUM> in the sliding hole <NUM> of the piston <NUM>, the flow path of the oil liquid is enlarged. When the sliding hole <NUM> of the piston <NUM> presses the oil liquid, the fluency of oil liquid transfer can be improved to reduce impediment of oil liquid to the piston <NUM> and the rotation shaft <NUM>, and the power consumption of the pump body assembly is reduced.

As shown in <FIG>, a plurality of the flexible grooves <NUM> are provided, and both ends of the same piston communication groove <NUM> are respectively provided with one flexible grooves <NUM>, wherein in the axial direction of the rotation shaft <NUM>, the ends of the flexible groove <NUM> go through the end faces on both ends of the piston <NUM>, such that a sliding boss <NUM> protruding from the hole wall face of the sliding hole <NUM> is formed within the sliding hole <NUM>.

Specifically, a surface of the sliding boss <NUM> facing towards a middle portion of the sliding hole <NUM> is a sliding face <NUM>. The sliding face <NUM> is a plane. During running of the pump body assembly, the sliding face <NUM> and the rotation shaft <NUM> are in sliding fit with each other to achieve the oil pressing process. By cooperation of the piston communication groove <NUM> and the flexible groove <NUM>, the fluency of oil liquid transfer is improved, the impediment of oil liquid to the piston <NUM> and the rotation shaft <NUM> is reduced, and the power consumption of the pump body assembly is reduced.

As shown in <FIG>, the flexible groove <NUM> has a length H3 greater than or equal to <NUM> and less than or equal to <NUM>. When the length H3 of the flexible groove <NUM> is less than <NUM>, the flexible groove <NUM> is too small and thus is not conducive to improve the fluency of oil liquid. When the length H3 of the flexible groove <NUM> is greater than <NUM>, the strength of the sliding boss <NUM> is affected and the sliding boss <NUM> is prone to be damaged during sliding fit with the rotation shaft <NUM>.

As shown in <FIG>, an included angle A between a surface of the flexible groove <NUM> near a middle portion of the sliding hole <NUM> and the hole wall face on a side where the flexible groove <NUM> is located in the sliding hole <NUM> ranges from <NUM>° to <NUM>°. If the included angle A is too large, the strength of the portion where the flexible groove <NUM> on the sliding boss <NUM> is located will be affected, and the sliding boss <NUM> is prone to be damaged during sliding fit with the rotation shaft <NUM>. If the included angle A is too small, it can't improve the fluency of oil liquid transfer, reduce impediment of oil liquid to the piston <NUM> and the rotation shaft <NUM>, and reduce power consumption of the pump body assembly.

As shown in <FIG>, the flexible groove <NUM> comprises a first groove surface and a second groove surface which are connected in sequence in a direction close to a middle portion of the sliding hole <NUM>, a first transition fillet ∠<NUM> is formed between the first groove surface and the hole wall face of the sliding hole <NUM>, a second transition fillet ∠<NUM> is formed between the second groove surface and the first groove surface, and a third transition fillet ∠<NUM> is formed at an edge on a side of the second groove surface far away from first groove surface.

Specifically, the first transition fillet ∠<NUM> is <NUM>°-<NUM>°, the second transition fillet z2 is <NUM>°-<NUM>°, and the third transition fillet ∠<NUM> is <NUM>°-<NUM>°. By setting the fillet and the corresponding angle ranges, the flowability of oil liquid is improved and the power consumption of the pump body assembly is reduced, without affecting the strength of the sliding boss <NUM>. The disposed fillet facilitates reducing the concentrated stress on the sliding boss <NUM> and enables stable running during the oil pressing process.

It should be noted that the piston <NUM> may also be formed by 3D printing technology, with a large hollow inside as machined and an outer housing, which can not be formed by general machining. The inner wall of the sliding hole <NUM> is provided with a piston communication groove <NUM> in an irregular shape. The piston communication groove <NUM> has a first width equal to <NUM>%-<NUM>% of a width W <NUM> of the piston <NUM>, the piston communication groove <NUM> has a second width equal to <NUM>%-<NUM>% of a width W1 of the piston <NUM>, and the piston communication groove <NUM> has a wall thickness of <NUM>-<NUM>.

As shown in <FIG>, the piston communication groove <NUM> has a width H1 accounting for <NUM>%-<NUM>% of a width W1 of the piston <NUM>. Specifically, when the width H1 of the piston communication groove <NUM> is too small, the fluency of oil liquid transfer during the oil pressing process cannot be effectively improved and the effect of reduction in power consumption of the pump body assembly cannot be achieved. When the width H1 of the piston communication groove <NUM> is too large, the strength of the rotation shaft <NUM> will be affected, and the rotation shaft <NUM> is prone to break during its movement with respect to the piston <NUM>.

As shown in <FIG>, <FIG>, the piston communication groove <NUM> has a depth H2 accounting for <NUM>%-<NUM>% of a width W1 of the piston <NUM>. Specifically, when the depth H2 of the piston communication groove <NUM> is too small, the fluency of oil liquid transfer during the oil pressing process cannot be effectively improved and the effect of reduction in power consumption of the pump body assembly cannot be achieved. When the depth H2 of the piston communication groove <NUM> is too large, the strength of the rotation shaft <NUM> will be affected, and the rotation shaft <NUM> is prone to break during its movement with respect to the piston <NUM>.

The pump body assembly in the present disclosure further comprises a cylinder sleeve <NUM> and a cylinder <NUM>, wherein the cylinder <NUM> is rotatably arranged in the cylinder sleeve <NUM> and the cylinder <NUM> is provided, in its radial direction, with a piston hole <NUM>, the piston <NUM> is slidably arranged in the piston hole <NUM>, the rotation shaft <NUM> penetrates through the piston <NUM> and drives the piston <NUM> to reciprocate in an extension direction of the piston hole <NUM>, and the cylinder <NUM> rotates to cause rotation of the piston <NUM>.

Specifically, in the process that the rotation shaft <NUM> drives the piston <NUM> to reciprocate in an extension direction of the piston hole <NUM>, the piston <NUM> presses the oil liquid to achieve the oil pressing process of the pump body assembly. The oil liquid is transferred within two cavities formed by the rotation shaft <NUM> with the piston <NUM> and the cylinder <NUM>. By setting the piston communication passage on the piston <NUM>, the impediment of the piston to oil liquid transfer during oil liquid flowing is reduced, thus reducing power consumption of the pump body assembly during the oil pressing process.

As can be seen from the above description, the above embodiment(s) of the present disclosure can achieve the following technical effect(s):.

By setting the piston communication passage(s) in the sliding hole <NUM> of the piston <NUM>, the fluency of oil liquid flow is improved and the power consumption of the pump body assembly is reduced. Currently, during running of a rotary cylinder compressor, when the rotation shaft <NUM> of the pump body assembly is sliding with respect to the piston <NUM>, an inner wall of the sliding hole <NUM> of the piston <NUM> will impede fluency of oil liquid flow when pressing the oil liquid and cause increase in power consumption of the pump body assembly.

Specifically, the rotation shaft <NUM> penetrates through the sliding hole <NUM> on the piston <NUM> and divides the portion inside the piston <NUM> into two cavities. During movement of the pump body assembly, the piston <NUM> reciprocates with respect to the rotation shaft <NUM>, and the two cavities increase and decrease periodically to achieve the oil pressing process. During the reciprocating movement of the piston <NUM>, the inner wall of the sliding hole <NUM> of the piston <NUM> will press the oil liquid to enable transfer of the oil liquid between the two cavities. The communication passage communicated with the sliding hole <NUM> is disposed on the piston <NUM> so as to improve fluency of oil liquid transfer, to decrease resistance to pressing oil liquid by the piston <NUM>, to reduce power consumption of the rotation shaft <NUM> and the piston <NUM> during the oil pressing process, and to reduce power consumption of the pump body assembly.

In order to solve the problem in prior art of impediment of the piston to oil liquid flow during use of rotary cylinder compressors, the cylinder <NUM> may be optimized, decreasing a gap between a stop convex ring <NUM> on the cylinder <NUM> and the rotation shaft <NUM> to reduce impediment of the stop convex ring <NUM> of the cylinder <NUM> to oil liquid and thus reduce power consumption of the pump body assembly.

Specifically, as shown in <FIG>, the pump body assembly comprises a cylinder <NUM> and a rotation shaft <NUM>, the cylinder <NUM> is rotatably arranged and the cylinder <NUM> is provided, in its axial direction, with a stop convex ring <NUM>; the rotation shaft <NUM> penetrates through the stop convex ring <NUM> and extends into the cylinder <NUM>, the stop convex ring <NUM> is provided, on an inner annular plane on a side facing towards the rotation shaft <NUM>, with an avoidance recess <NUM> such that a flow-through gap is formed between the rotation shaft <NUM> and the avoidance recess <NUM>.

As can be seen from the above description, in the above embodiment(s) of the present disclosure, by setting the avoidance recess <NUM> on the stop convex ring <NUM> of the cylinder <NUM> on the inner annular plane on the side facing towards the rotation shaft <NUM>, the flow-through gap between the rotation shaft <NUM> and the cylinder <NUM> is increased and the oil liquid resistance to the rotation shaft <NUM> and the piston <NUM> is reduced, thus improving running stability. Currently, in the prior pump body assembly, the flow-through gap formed between the rotation shaft <NUM> and the inner wall of the stop convex ring <NUM> on the cylinder <NUM> is too small, the piston <NUM> and the rotation shaft <NUM> are impeded by the oil liquid during movement, resulting in increased power consumption for oil pressing of the piston <NUM> and the rotation shaft <NUM> and also affecting stability of the rotation shaft <NUM> and the piston <NUM>.

Specifically, the rotation shaft <NUM> penetrates through the cylinder <NUM> and the flow-through gap is formed between the rotation shaft <NUM> and the inner annular plane of the stop convex ring <NUM> of the cylinder <NUM>. The avoidance recess <NUM> is disposed on the inner annular plane of the stop convex ring <NUM> to increase the flow-through gap between the rotation shaft <NUM> and the cylinder <NUM> to facilitate flow and transfer of oil liquid, effectively reducing oil liquid resistance to the rotation shaft <NUM> and the piston <NUM> during rotation, and preventing the rotation shaft <NUM> and the piston <NUM> from increase of power consumption or being unstable due to impediment of oil liquid to the rotation shaft <NUM> and the piston <NUM>.

As shown in <FIG>, the avoidance recess <NUM> extends to edges on both sides of the stop convex ring <NUM> in the axial direction of the rotation shaft <NUM>.

Specifically, the avoidance recess <NUM> extends to the edges on both sides of the stop convex ring <NUM> to form a gap passage, enlarging the flow-through gap, improving fluency of the oil liquid flowing through the flow-through gap, reducing impediment of oil liquid to the rotation shaft <NUM>, and reducing power consumption of the pump body assembly.

As shown in <FIG>, the avoidance recess <NUM> is an avoidance groove disposed on an inner annular face such that the wall thickness of the portion of the stop convex ring <NUM> with the hiding groove is less than that of the portion of the stop convex ring <NUM> without the hiding groove.

Specifically, the avoidance recess <NUM> is a hiding groove disposed on an inner annular face. The hiding groove is provided to increase the flow-through gap at the hiding groove. During the oil pressing process of the pump body assembly, when the oil liquid is pressed to flow through the hiding groove, the impediment to the oil liquid can be reduced, improving fluency of oil liquid flow and reducing power consumption of the pump body assembly.

In the present disclosure, the flow-through gap is greater than <NUM> and less than <NUM>. The flow-through gap controlled to be within the range from <NUM> to <NUM> can effectively improve fluency of oil liquid flow and reduce power consumption of the pump body assembly. When the flow-through gap is less than <NUM>, it is too small to improve fluency of oil liquid flowing through the flow-through gap and cannot achieve the effect of reduction in power consumption of the pump body assembly. When the flow-through gap is greater than <NUM>, it is too large and will affect the strength of the portion at the stop convex ring <NUM> of the cylinder <NUM>, and thus the stop convex ring <NUM> is prone to be damaged, resulting in that the problems of inclination and oil leakage are prone to occur to the cylinder <NUM> during running.

Specifically, the avoidance recess <NUM> has a width in a circumferential direction of the inner annular face which equals to <NUM>%-<NUM>% of a diameter of the inner annual face. When the width of avoidance recess <NUM> in the circumferential direction of the inner annular face is too small, the width of the flow-through gap formed at the avoidance recess <NUM> is too small, the fluency of the oil liquid flowing through the flow-through gap cannot be effectively improved, and the effect of reduction in power consumption of the pump body assembly cannot be achieved. When the width of avoidance recess <NUM> in the circumferential direction of the inner annular face is too large, the stability of the stop convex ring <NUM> of the cylinder <NUM> will be affected, resulting in that the problems of inclination and oil leakage are prone to occur to the cylinder <NUM> during running, and also affecting stable running of the pump body assembly.

It should be noted that the width of the avoidance recess <NUM> in the circumferential direction of the inner annular face may be changed according to the size of the stop convex ring <NUM> on the cylinder <NUM>. For different types of cylinders <NUM>, the corresponding avoidance recesses <NUM> having different widths may be provided on the inner annular face of the stop convex ring <NUM> of the cylinder <NUM>.

As shown in <FIG>, the flow-through gap is <NUM>%-<NUM>% of the diameter of the inner annular face. Specifically, when the pump body assembly is pressing oil, the oil liquid can flow through the flow-through gap to reduce impediment of the stop convex ring <NUM> to the oil liquid, thus improving fluency of oil liquid flow and reducing power consumption during the oil pressing process of the pump body. When the flow-through gap is too small, it is too small to improve fluency of the oil liquid flowing through the flow-through gap and cannot achieve the effect of reduction in power consumption of the pump body assembly. When the flow-through gap is too large, it will affect the strength of the portion at the stop convex ring <NUM> of the cylinder <NUM>, and thus the stop convex ring <NUM> is prone to be damaged, resulting in that the problems of inclination and oil leakage are prone to occur to the cylinder <NUM> during running, and also affecting stable running of the pump body assembly.

It should be noted that the flow-through gap may be varied according to the size of the stop convex ring <NUM> on the cylinder <NUM>. For different types of cylinders <NUM>, the corresponding flow-through gaps may be provided on the inner annular face of the stop convex ring <NUM> of the cylinder <NUM>.

As shown in <FIG>, the stop convex ring <NUM> has a minimum wall thickness t greater than or equal to <NUM> at the portion where the avoidance recess <NUM> is located. With the stop convex ring <NUM> having the wall thickness greater than or equal to <NUM>, during rotation of the cylinder <NUM>, the stop convex ring <NUM> has a function of positioning. The stop convex ring <NUM> has an influence on the stability of the cylinder <NUM> and prevents the cylinder <NUM> from inclination. The stop convex ring <NUM> is robust. Therefore, the stop convex ring <NUM> has a minimum wall thickness t greater than or equal to <NUM> to ensure strength of the stop convex ring <NUM> such that the cylinder <NUM> can run stably.

As shown in <FIG>, <FIG>, <FIG>, <FIG>, the cylinder <NUM> is provided thereon, in its radial direction, with a piston hole <NUM>. The inner annular face of the stop convex ring <NUM> has a first face segment <NUM> and a second face segment <NUM> opposite thereto. A connection line of the first face segment <NUM> and the second face segment <NUM> is perpendicular to an extension direction of the piston hole <NUM>. Each of the first face segment <NUM> and the second face segment <NUM> is provided with the avoidance recess <NUM>.

Specifically, the connection line of the first face segment <NUM> and the second face segment <NUM> of the stop convex ring <NUM> of the cylinder <NUM> is perpendicular to the extension direction of the piston hole <NUM> on the cylinder <NUM>. The oil liquid flows through the first face segment and the second face segment. Each of the first face segment <NUM> and the second face segment <NUM> is provided thereon with the avoidance recess <NUM>. It can improve fluency of oil liquid at the flow-through gap, facilitate oil liquid transfer, and thus reduce power consumption of the pump body assembly.

It should be noted that during mounting of the pump body assembly, the rotation shaft <NUM> may be close to the first face segment or to the second face segment. Each of the first face segment and the second face segment is provided thereon with the avoidance recess <NUM>. Therefore, when the rotation shaft <NUM> is close to either the first face segment or the second face segment, the same technical effect can be achieved, both improving fluency of oil liquid and facilitating mounting.

As shown in <FIG>, the pump body assembly further comprises a piston <NUM> provided with a sliding hole <NUM>, the rotation shaft <NUM> penetrates through the sliding hole <NUM>, and a group of face segments of the inner annular face of the stop convex ring <NUM> in the extension direction of the sliding hole <NUM> are each provided with the avoidance recess <NUM>.

Specifically, the piston <NUM> is provided thereon with a sliding hole <NUM>. The piston <NUM> moves within the cylinder <NUM> to achieve oil pressing. The piston <NUM> presses the oil liquid to enable oil liquid transfer. The oil liquid pressed by the piston <NUM> will flow through a group of face segments of the stop convex ring <NUM> in the extension direction of the sliding hole <NUM>. The face segments is provided thereon with the avoidance recess <NUM>. It can reduce oil pressing resistance to the piston <NUM>, reduce vibration of the piston <NUM>, and avoid the problem of damage to the piston <NUM>. Also, the avoidance recess <NUM> improves fluency of oil liquid flow, reduces resistance between the rotation shaft <NUM> and the oil liquid, and reduces power consumption of the pump body assembly. Herein, just another reference is used. The extension direction of the piston hole <NUM> is previously used as reference, while the extension direction of the sliding hole <NUM> is herein used as reference, wherein the extension direction of the piston hole <NUM> may be same as or perpendicular to the extension direction of the sliding hole <NUM>. Specifically, it is apparent in <FIG> that the extension direction of the piston hole <NUM> is perpendicular to that of the sliding hole <NUM>.

As shown in <FIG>, the pump body assembly further comprises a cylinder sleeve <NUM> having a volume cavity <NUM>. The cylinder <NUM> is rotatably arranged in the volume cavity <NUM>. The piston <NUM> is slidably arranged in the piston hole <NUM> of the cylinder <NUM>. The rotation shaft <NUM> penetrates through the sliding hole <NUM> of the piston <NUM> and drives the piston <NUM> to reciprocate in an extension direction of the piston hole <NUM>. The cylinder <NUM> rotates to cause rotation of the piston <NUM>.

Specifically, the cylinder <NUM> and the rotation shaft <NUM> rotate. The cylinder <NUM> can cause the piston <NUM> to rotate. The rotation shaft <NUM> penetrates through the sliding hole <NUM> of the piston <NUM> and divides a volume cavity <NUM> inside the cylinder <NUM> and the piston <NUM> into two cavities. With the action of the rotation shaft <NUM>, the piston <NUM> reciprocates within the piston hole <NUM> in the extension direction of the piston hole <NUM>. The reciprocating movement of the piston <NUM> causes the two cavities to increase and decrease periodically. Also, the piston <NUM> presses the oil liquid within the cylinder <NUM> to achieve periodical transfer of the oil liquid within the two cavities. By setting the avoidance recess <NUM> on the inner annular face of the stop convex ring <NUM> of the cylinder <NUM>, the impediment of the stop convex ring <NUM> to the oil liquid during transfer of the oil liquid can be reduced, improving fluency of oil liquid transfer and reducing power consumption of the pump body assembly.

By setting the avoidance recess <NUM> on the stop convex ring <NUM> of the cylinder <NUM> on the inner annular plane on the side facing towards the rotation shaft <NUM>, the flow-through gap between the rotation shaft <NUM> and the cylinder <NUM> is increased and the oil liquid resistance to the rotation shaft <NUM> and the piston <NUM> is reduced, thus improving running stability. Currently, in the prior pump body assembly, the flow-through gap formed between the rotation shaft <NUM> and the inner wall of the stop convex ring <NUM> on the cylinder <NUM> is too small, the piston <NUM> and the rotation shaft <NUM> are impeded by the oil liquid during movement, resulting in increased power consumption for oil pressing of the piston <NUM> and the rotation shaft <NUM> and also affecting stability of the rotation shaft <NUM> and the piston <NUM>.

Specifically, the rotation shaft <NUM> penetrates through the cylinder <NUM> and the flow-through gap is formed between the rotation shaft <NUM> and the inner annular plane of the stop convex ring <NUM> of the cylinder <NUM>. The avoidance recess <NUM> is disposed on the inner annular plane of the stop convex ring <NUM> to increase the flow-through gap between the rotation shaft <NUM> and the cylinder <NUM> to facilitate flow and transfer of oil liquid, it can effectively reduce oil liquid resistance to the rotation shaft <NUM> and the piston <NUM> during rotation, and prevent the rotation shaft <NUM> and the piston <NUM> from producing increased power consumption or being unstable due to impediment of oil liquid to the rotation shaft <NUM> and the piston <NUM>.

In order to solve the problem in prior art of impediment to oil liquid flow during use of rotary cylinder compressors, it is possible to optimize the rotation shaft <NUM> so as to reduce impediment of the rotation shaft <NUM> to the fluency of oil liquid flow in the piston <NUM>, thereby reducing power consumption of the pump body assembly.

Specifically, as shown in <FIG>, a pump body assembly comprises a rotation shaft <NUM> and a piston <NUM> provided with a sliding hole <NUM>, with at least a portion of the rotation shaft <NUM> penetrating into the sliding hole <NUM>, during rotation of the piston <NUM> with the rotation shaft <NUM>, the sliding hole <NUM> is in sliding fit with the rotation shaft <NUM>, wherein the rotation shaft <NUM> is provided, on the shaft segment of the rotation shaft <NUM> in the sliding hole <NUM>, with a rotation shaft flow-through passage, and the rotation shaft flow-through passage extends in the sliding direction of the piston <NUM>.

As can be seen from the above description, in the above embodiment(s) of the present disclosure, the rotation shaft <NUM> is provided, on the shaft segment of the rotation shaft <NUM> in the sliding hole <NUM> of the piston <NUM>, with a flow-through passage, the fluency of oil liquid flow is improved and the power consumption of the pump body assembly is reduced. Currently, during running of a rotary cylinder compressor, when the rotation shaft of the pump body assembly is sliding with respect to the piston, the region of the rotation shaft in the piston impedes flowing of the oil liquid such that the oil liquid impedes movement of the piston and the rotation shaft and the power consumption of the pump body assembly is increased.

Specifically, the rotation shaft <NUM> penetrates through the sliding hole <NUM> on the piston <NUM> and divides the portion inside the piston <NUM> into two cavities. During movement of the pump body assembly, the piston <NUM> reciprocates with respect to the rotation shaft <NUM>, and the two cavities increase and decrease periodically to achieve the oil pressing process. The shaft segment of the rotation shaft <NUM> in the sliding hole <NUM> of the piston <NUM> will press the oil liquid to enable transfer of the oil liquid within the two cavities. The rotation shaft flow-through passage is disposed on the shaft segment of the rotation shaft <NUM> in the sliding hole <NUM> so as to reduce impediment of the rotation shaft <NUM> to the oil liquid and reduce power consumption of the piston <NUM> and the rotation shaft <NUM> during the oil pressing process, and thus reduce power consumption of the pump body assembly.

As shown in <FIG> and <FIG>, there are a plurality of rotation shaft flow-through passages which are spaced in the axial direction of the rotation shaft <NUM>. By setting a plurality of spaced rotation shaft flow-through passages on the rotation shaft <NUM>, during the oil pressing process, the oil liquid can be transferred via the plurality of rotation shaft flow-through passages, enlarging the flow path and reducing power consumption of the piston <NUM> and the rotation shaft <NUM> during the oil pressing process.

In some embodiments, there are less than <NUM> rotation shaft flow-through channels. When there are more than <NUM> flow-through passages, too many rotation shaft flow-through passages will cause decrease in strength of the rotation shaft <NUM>, and during relative movement of the rotation shaft <NUM> and the piston <NUM>, the rotation shaft <NUM> is prone to break due to decrease in strength of the rotation shaft <NUM>. With less than <NUM> rotation shaft flow-through passages, the flow path of the oil liquid is enlarged, without affecting the strength of the rotation shaft <NUM>.

It should be noted that in the specific embodiments as shown in <FIG>, the rotation shaft flow-through passage is a passage disposed on the rotation shaft <NUM> to enlarge the flow path of the oil liquid. In the specific implementation(s), there may be multiple specific structures for the rotation shaft flow-through passage as long as the impediment of the rotation shaft <NUM> to the oil transfer in the sliding hole <NUM> of the piston <NUM> can be reduced, and they will not be described herein one by one.

Hereinafter, according to different structures for the rotation shaft flow-through passage, the following specific implementations are provided for explanation.

In the specific implementations as shown in <FIG>, the sliding hole <NUM> has a group of opposite hole wall faces of the sliding hole <NUM>. The rotation shaft <NUM> is provided, on the shaft segment in the sliding hole <NUM>, with a sliding fit face <NUM> cooperating with the hole wall face of the sliding hole <NUM>. The rotation shaft flow-through passage is a rotation shaft communication groove <NUM> and is disposed on the sliding fit face <NUM>.

Specifically, when the rotation shaft <NUM> moves with respect to the sliding hole <NUM> of the piston <NUM>, the sliding fit face <NUM> on the rotation shaft <NUM> is used to be in relative sliding fit with the hole wall face on the sliding hole <NUM>. The rotation shaft communication groove <NUM> is disposed on the sliding fit face <NUM>. The sliding fit face <NUM> presses the oil liquid during sliding relative to the hole wall face of the sliding hole <NUM>. The oil liquid can be transferred via the rotation shaft communication groove <NUM>, decreasing resistance between the rotation shaft <NUM> and the piston <NUM> and the oil liquid, and reducing power consumption of the pump body assembly.

It should be noted that the sliding fit face <NUM> is a plane. This means that the hole wall face of the sliding hole <NUM> is a plane. The sliding fit face <NUM> reciprocates with respect to the hole wall face of the sliding hole <NUM>. The rotation shaft communication groove <NUM> is provided on a surface of the sliding fit face <NUM>.

As shown in <FIG> and <FIG>, the rotation shaft communication groove <NUM> has a width t1 accounting for <NUM>%-<NUM>% of a diameter R1 of the shaft segment of the rotation shaft <NUM> in the sliding hole <NUM>. When the width t1 of the rotation shaft communication groove <NUM> is too small, it cannot effectively improve fluency of oil liquid transfer during the oil pressing process and the effect of reduction in power consumption of the pump body assembly cannot be achieved. When the width t1 of the rotation shaft communication groove <NUM> is too large, the strength of the rotation shaft <NUM> will be affected and the rotation shaft <NUM> is prone to break during its movement with respect to the piston <NUM>.

It should be noted that the width t1 of the rotation shaft communication groove <NUM> may be varied according to different types of the rotation shaft <NUM> as long as the fluency of oil liquid can be improved and the power consumption of the pump body assembly during the oil pressing process can be reduced.

As shown in <FIG> and <FIG>, the rotation shaft communication groove <NUM> has a depth h1 accounting for <NUM>%-<NUM>% of a diameter R1 of the shaft segment of the rotation shaft <NUM> in the sliding hole <NUM>.

Specifically, when the depth h1 of the rotation shaft communication groove <NUM> is too small, it cannot effectively improve fluency of oil liquid transfer during the oil pressing process and the effect of reduction in power consumption of the pump body assembly cannot be achieved. When the depth h1 of the rotation shaft communication groove <NUM> is too large, the strength of the rotation shaft <NUM> will be affected and the rotation shaft <NUM> is prone to break during its movement with respect to the piston <NUM>.

It should be noted that the depth h1 of the rotation shaft communication groove <NUM> may be varied according to different types of the rotation shaft <NUM> as long as the fluency of oil liquid can be improved and the power consumption of the pump body assembly during the oil pressing process can be reduced.

In the specific implementation as shown in <FIG>, the sliding hole <NUM> has a group of opposite hole wall faces of the sliding hole <NUM>. The rotation shaft <NUM> is provided, on the shaft segment in the sliding hole <NUM>, with a sliding fit face <NUM> cooperating with the hole wall face of the sliding hole <NUM>. The rotation shaft <NUM> is further provided, on the shaft segment in the sliding hole <NUM>, with a group of connection faces <NUM>, opposite to each other, for connecting two sliding fit faces <NUM>. The rotation shaft flow-through passage is a rotation shaft flow-through hole <NUM>, and rotation shaft flow-through hole <NUM> penetrates through two connection faces <NUM>.

Specifically, the rotation shaft <NUM> penetrates through the sliding hole <NUM> of the piston <NUM> and divides the sliding hole <NUM> into two cavities. During the oil pressing process, the oil liquid is transferred between the two cavities. The rotation shaft flow-through hole <NUM> is disposed between the two connection faces <NUM>, so as to improve fluency of oil liquid flow, reduce impediment of oil liquid to the rotation shaft <NUM> and the piston <NUM>, and reduce power consumption of the pump body assembly during the oil pressing process.

It should be noted that the sliding fit face <NUM> is a plane such that a distance L1 between the two sliding fit faces <NUM> is greater than a diameter of the rotation shaft flow-through hole <NUM> by <NUM>. The sliding fit face <NUM> slides with respect to the hole wall face of the sliding hole <NUM>, with the friction reduced by the planar design, and the distance L1 between the two sliding fit faces <NUM> is greater than the diameter of the rotation shaft flow-through hole <NUM> by <NUM>, to ensure the strength of the rotation shaft <NUM>, and prevent the rotation shaft <NUM> from damage or breaking during running due to a too large diameter of the rotation shaft flow-through hole <NUM>.

In some embodiments, the diameter of the rotation shaft flow-through hole <NUM> is greater than or equal to <NUM>. when the diameter of the rotation shaft flow-through hole <NUM> is less than <NUM>, the effect of reducing pump body assembly cannot be achieved. In order to improve fluency of oil liquid flow, it is necessary for the diameter of the rotation shaft flow-through hole to be greater than or equal to <NUM>.

As shown in <FIG> and <FIG>, the rotation shaft <NUM> comprises a long shaft segment <NUM> and a short shaft segment <NUM> which are connected in sequence, with the long shaft segment <NUM> having a length greater than that of the short shaft segment <NUM>. The long shaft segment <NUM> is provided thereon with a sliding fit face <NUM>. At least a portion of the long shaft segment <NUM> extends into the sliding hole <NUM>.

Specifically, the sliding fit face <NUM> on the long shaft segment <NUM> is in sliding fit with the hole wall face of the sliding hole <NUM> in the piston <NUM>. The rotation shaft flow-through passage is disposed on the long shaft segment <NUM> to achieve reduction in power consumption of the rotation shaft <NUM> and the piston <NUM> during the oil pressing process.

As shown in <FIG>, <FIG>, the diameter of the shaft segment in the sliding hole <NUM> is greater than the diameter of the short shaft segment <NUM>. A stepped shape is formed at an interface between an end face of the shaft segment and the short shaft segment <NUM>, and a support face is formed at an interface between the end face of the shaft segment and the short shaft segment <NUM>.

The pump body assembly in the present disclosure further comprises a cylinder sleeve <NUM>, and a cylinder <NUM> is rotatably arranged in the cylinder sleeve <NUM>. The cylinder <NUM> is provided thereon, in its radial direction, with a piston hole <NUM>. The piston <NUM> is slidably arranged in the piston hole <NUM>. The rotation shaft <NUM> penetrates through the piston <NUM> and drives the piston <NUM> to reciprocate in an extension direction of the piston hole <NUM>. The cylinder <NUM> rotates to cause rotation of the piston <NUM>.

Specifically, during the reciprocating movement of the piston <NUM> in the extension direction of the piston hole <NUM> driven by the rotation shaft <NUM>, the piston <NUM> presses the oil liquid to achieve the oil pressing process of the pump body assembly. The oil liquid is transferred within the two cavities formed by the rotation shaft <NUM> and the piston <NUM> and the cylinder <NUM>. The rotation shaft flow-through passage is disposed on the shaft segment of the rotation shaft <NUM>, so as to improve fluency of oil liquid transfer, to reduce impediment of the rotation shaft <NUM> to oil liquid transfer during flowing of the oil liquid and reduce power consumption of the pump body assembly during the oil pressing process.

As can be seen from the above description, in the above embodiments of the present disclosure, the following technical effects are achieved:.

The flow-through passage is disposed on the shaft segment of the rotation shaft <NUM> in the sliding hole <NUM> of the piston <NUM>, so as to improve fluency of oil liquid flow and reduce power consumption of the pump body assembly. Currently, during running of a rotary cylinder compressor, when the rotation shaft <NUM> of the pump body assembly is sliding with respect to the piston <NUM>, the region of the rotation shaft <NUM> in the piston <NUM> impedes flowing of the oil liquid such that the oil liquid impedes movement of the piston <NUM> and the rotation shaft <NUM> and the power consumption of the pump body assembly is increased.

In order to solve the problem in prior art of impediment to oil liquid flow during use of rotary cylinder compressors, a flange structure can be optimized to reduce impediment of the flange structure to the piston <NUM>, thereby improving fluency of oil liquid flow to reduce power consumption of the pump body assembly.

Specifically, as shown in <FIG>, the pump body assembly comprises a cylinder <NUM> and a flange structure. The cylinder <NUM> is rotatably arranged. The flange structure is on a side of the cylinder <NUM> and has a positioning boss <NUM> protruding in the cylinder <NUM>. The positioning boss <NUM> is provided thereon with an avoidance recess <NUM>.

As can be seen from the above description, in the above embodiment(s) of the present disclosure, the avoidance recess <NUM> is disposed on the positioning boss <NUM> to reduce impediment of the flange structure to the flow path and reduce power consumption of the compressor. Currently, the flange structure of the prior pump body seriously blocks the path in the flow path in the cylinder <NUM> and the piston <NUM> close to the side of the flange structure such that the frozen oil cannot be smoothly transferred in the flow path, resulting in increase in resistance to the rotation shaft <NUM> during rotation and increase in power consumption of the compressor. Specifically, when the flange structure is the lower flange <NUM>, the portion in the flow path close to the lower portion is prone to be blocked.

Specifically, the positioning boss <NUM> of the flange structure protrudes in the cylinder <NUM>. By setting the avoidance recess <NUM> on the positioning boss <NUM>, the impediment of the positioning boss <NUM> to the flow path in the cylinder <NUM> is reduced. During rotation of the cylinder <NUM>, the oil liquid in the cylinder <NUM> flows back and forth via the flow path in the cylinder <NUM>. When the oil liquid flows to the positioning boss <NUM>, the oil liquid can flow along the avoidance recess <NUM>, increasing the flow volume, thus reducing power consumption of the compressor and also reducing noise and vibration of the compressor.

As shown in <FIG>, the positioning boss <NUM> is concentric with the flange structure. The positioning boss <NUM> is formed integrally on the flange structure and is partially protruded in the cylinder <NUM> to position the cylinder <NUM> to prevent the cylinder <NUM> from inclination during rotation. Also, the flange structure has a load bearing ability. When the positioning boss <NUM> is concentric with the flange structure, the eccentric force between the positioning boss <NUM> and the flange structure is decreased and the stability of the flange structure and the positioning boss <NUM> is increased, thus improving running stability of the pump body assembly and also prolonging the service lives of the flange structure and the positioning boss <NUM>.

As shown in <FIG>, the flange structure further comprises a flange hole <NUM> penetrating through the positioning boss <NUM>. The flange hole <NUM> is eccentric with respect to the center of the flange structure. The pump body assembly further comprises a rotation shaft <NUM> penetrating through the cylinder <NUM> and the flange hole <NUM>.

Specifically, the rotation shaft <NUM> penetrates through the piston <NUM> and the cylinder <NUM>, and is inserted in the flange hole <NUM>. Herein, the flange hole <NUM> is eccentric with respect to the positioning boss <NUM>. The positioning boss <NUM> has a function of bearing the rotation shaft <NUM>, and thus the eccentric flange hole <NUM> can effectively decrease the concentrated stress between the positioning boss <NUM> and the flange structure, which is conducive to prolonging the service life of the flange structure and also convenient to provide the avoidance recess <NUM> on the positioning boss <NUM>. The avoidance recess <NUM> enlarges the flow path of the oil liquid, decreases resistance of the oil liquid to the rotation shaft <NUM>, and reduces power consumption of the pump body assembly.

As shown in <FIG>, the positioning boss <NUM> is in a shape of step, and comprises a first segment <NUM> and a second segment <NUM>. The first segment <NUM> is far away from the center of the cylinder <NUM> than the second segment <NUM>. The outer circumferential face of the first segment <NUM> is matched with an inner wall face of the cylinder <NUM>. a surface of the second segment <NUM> on the side facing towards the center of the cylinder <NUM> is used as a support face for supporting the rotation shaft <NUM> of the pump body assembly. The flange hole <NUM> penetrates through the first segment <NUM> and the second segment <NUM>.

Specifically, the second segment <NUM> and the first segment <NUM> cooperate to form a structure in stepped shape. The outer circumferential face of the first segment <NUM> and the inner surface of the cylinder <NUM> are matched, without affecting rotation of the cylinder <NUM>. An end face of the second segment <NUM> facing towards the center of the cylinder <NUM> supports the rotation shaft <NUM>. The flange hole <NUM> and the second segment <NUM> are concentric. The first segment <NUM> and the second segment <NUM> cooperate to form the avoidance recess <NUM>, thus enlarging the flow path in the cylinder <NUM>, reducing impediment to rotation of the rotation shaft <NUM>, and reducing power consumption of the pump body assembly.

It should be noted that in the specific embodiments as shown in <FIG>, the first segment <NUM> and the second segment <NUM> are both circular bosses. During practical production, it is not necessary for both the first segment <NUM> and the second segment <NUM> to be circular bosses. It is also possible that only one of the first segment <NUM> and the second segment <NUM> is a circular boss, or it is also possible that none of the first segment <NUM> and the second segment <NUM> is a circular boss, as long as the first segment <NUM> can be matched with the inner face of the cylinder <NUM> without any impediment and the second segment <NUM> can support the rotation shaft <NUM>. As there are various shapes and combination forms for the first segment <NUM> and the second segment <NUM>, no further specific embodiment will be additionally provided herein for explanation.

It should be noted that based on difference in position as disposed for the second segment <NUM> with respect to the first segment <NUM>, it is possible to form various shapes of the avoidance recess <NUM>. As there are various shape combination forms for the, the combination forms will not be described one by one. Hereinafter, according to different shapes for the avoidance recess <NUM>, different implementations are provided respectively for explanation.

In the specific implementations as shown in <FIG>, the first segment <NUM> and the second segment <NUM> are both circular bosses. The orthographic projection of the second segment <NUM> on the first segment <NUM> is not completely overlapped with the outer circumference of the first segment <NUM>, and the avoidance recess <NUM> is formed at a stepped face between the outer circumference of the second segment <NUM> and the first segment <NUM>. In this case, the avoidance recess <NUM> is a recess in a crescent shape which has an outer circle concentric with the flange structure.

Specifically, the first segment <NUM> and the second segment <NUM> are both circular bosses. As the avoidance recess <NUM> is formed at the stepped face between the outer circumference of the second segment <NUM> and the first segment <NUM>, when the outer circumference of the second segment <NUM> is partially overlapped with the outer circumference of the first segment <NUM>, the avoidance recess <NUM> in a crescent shape is formed at the stepped face between the outer circumference of the second segment <NUM> and the first segment <NUM>. The avoidance recess <NUM> in the crescent shape enlarges the flow path of the oil liquid, reduces impediment of the oil liquid to the rotation shaft <NUM>, and reduces power consumption of the pump body assembly.

In the specific implementation as shown in <FIG>, the first segment <NUM> and the second segment <NUM> are both circular bosses. The orthographic projection of the second segment <NUM> on the first segment <NUM> is not completely overlapped with the outer circumference of the first segment <NUM>. The first segment <NUM> is further disposed thereon with a support rib <NUM> extending towards a center of the cylinder <NUM>. The support rib <NUM> is not higher than the second segment <NUM>. At least one side surface of the support rib <NUM> is flush with the outer circumference of the first segment <NUM>. The support rib <NUM> and the second segment <NUM> are spaced apart, and the avoidance recess <NUM> is formed between the support rib <NUM> and the second segment <NUM>. In this case, the avoidance recess <NUM> has an irregular shape. Herein, in the specific embodiment(s), it is generally possible to select the support rib <NUM> having a height same as that of the second segment <NUM>.

Specifically, with the support rib <NUM> disposed on the first segment <NUM>, the support rib <NUM>, the first segment <NUM> and the second segment <NUM> cooperate to form the avoidance recess <NUM> in an irregular shape. The avoidance recess <NUM> can enlarge the flow path in the cylinder <NUM>, decrease resistance between the rotation shaft <NUM> and the oil liquid, and reduce power consumption of the pump body assembly. Moreover, with the support rib <NUM> added, the stability between the positioning boss <NUM> and the cylinder <NUM> can be improved.

It should be noted that the area of the irregular shape is determined as being not greater than an end area of an end of the first segment <NUM> facing towards the center of the cylinder <NUM>.

In the specific implementation as shown in <FIG>, the first segment <NUM> and the second segment <NUM> are both circular bosses. The orthographic projection of the second segment <NUM> on the first segment <NUM> is not completely overlapped with the outer circumference of the first segment <NUM>. The first segment <NUM> is further disposed thereon with a support rib <NUM> extending towards a center of the cylinder <NUM>. The support rib <NUM> is not higher than the second segment <NUM>. At least one side surface of the support rib <NUM> is flush with the outer circumference of the first segment <NUM>. The support rib <NUM> and the second segment <NUM> are at least partially connected, and the avoidance recess <NUM> is formed between the support rib <NUM> and the second segment <NUM>. In this case, the avoidance recess <NUM> has a crescent shape, and the outer circle of the crescent shape is eccentric with respect to the flange structure.

Specifically, with the support rib <NUM> added between the second segment <NUM> and the first segment <NUM>, the stability between the positioning boss <NUM> and the cylinder <NUM> can be improved, preventing the cylinder <NUM> from inclination. Moreover, the avoidance recess <NUM> formed between the first segment <NUM> and the second segment <NUM> can enlarge the flow path in the cylinder <NUM>, decrease resistance between the rotation shaft <NUM> and the oil liquid, and reduce power consumption of the pump body assembly.

In a specific embodiment not shown, the first segment <NUM> and the second segment <NUM> are both circular bosses. The orthographic projection of the second segment <NUM> on the first segment <NUM> is not overlapped at all with the outer circumference of the first segment <NUM> such that an avoidance recess <NUM> is formed at a stepped face between the outer circumference of the second segment <NUM> and the first segment <NUM>. In this case, the avoidance recess <NUM> is an annular recess.

Specifically, the first segment <NUM> is not overlapped with the outer circumference of the second segment <NUM>. An annular avoidance recess <NUM> is formed at a stepped face between the outer circumference of the second segment <NUM> and the first segment <NUM>. The annular avoidance recess <NUM> can enlarge the flow path, reduce impediment of the flange structure to the flow path, and reduce power consumption of the pump body assembly.

It should be noted that when the avoidance recess <NUM> is an annular recess, it is possible for the inner and outer annular faces thereof to be concentric or eccentric. When the inner and outer annular faces are concentric or eccentric, the same technical effect can be achieved. That is, the annular avoidance recess <NUM> can enlarge the flow path and reduce impediment of the rotation shaft <NUM> to the oil liquid. Therefore, the configuration of the inner and outer annular faces, either concentric or eccentric, will not be individually described herein.

As shown in <FIG>, the avoidance recess <NUM> has a depth h equal to <NUM>%-<NUM>% of a diameter of the first segment <NUM>. Specifically, the depth of the avoidance recess <NUM> is limited by the diameter of the first segment <NUM>, to prevent a too large depth of the avoidance recess <NUM> from affecting stability of cooperation of the positioning boss <NUM> and the flange structure with the rotation shaft <NUM> and the cylinder <NUM>. When the depth h of the avoidance recess <NUM> equals to <NUM>%-<NUM>% of the diameter of the first segment <NUM>, the avoidance recess <NUM> can enlarge the flow path of the oil liquid, decrease resistance to rotation of the rotation shaft <NUM>, and reduce power consumption, without affecting running stability of the pump body assembly.

As shown in <FIG>, a wall thickness d of the second segment <NUM> is <NUM>%-<NUM>% of a maximum wall thickness D of the first segment <NUM>. As the second segment <NUM> is eccentric with respect to the flange structure and the first segment <NUM> is concentric with respect to the flange structure, the second segment <NUM> is thus eccentric with respect to the first segment <NUM>. It should be noted that when the wall thickness of the second segment <NUM> is <NUM>%-<NUM>% of the maximum wall thickness of the first segment <NUM>, the eccentricity ratio of the second section <NUM> to the first section <NUM> is constant, and will not change with the ratio of the wall thickness of the first segment <NUM> to the maximum wall thickness of the second segment <NUM>. Moreover, the wall thickness of the second segment <NUM> is constant while the wall thickness of the first segment <NUM> may be changed. By setting the avoidance recess <NUM> on the stepped face between the second segment <NUM> and the first segment <NUM>, the effect of enlarging flow path is achieved to reduce power consumption of the pump body.

In some embodiments, the second segment <NUM> has a wall thickness d equal to <NUM>%-<NUM>% of a maximum wall thickness D of the first segment <NUM>. Specifically, by further defining the wall thickness d of the second segment <NUM> and maximum wall thickness D of the first segment <NUM>, it can be seen that when the wall thickness d of the second segment <NUM> equals to <NUM>%-<NUM>% of the maximum wall thickness D of the first segment <NUM>, the flow-through effect of the oil liquid in the flow path is the best, the resistance of the oil liquid to the rotation shaft <NUM> is the lowest, and the power consumption of the pump body assembly is the lowest.

As shown in <FIG>, the avoidance recess <NUM> has a depth h equal to <NUM>%-<NUM>% of a height H of the flange structure. Specifically, when the depth h of the avoidance recess <NUM> is less than <NUM>%-<NUM>% of the height H of the flange structure, the depth of the avoidance recess <NUM> on the positioning boss <NUM> is too small, the first segment <NUM> of the positioning boss <NUM> will impede flow of the oil liquid in the flow path and the oil liquid will impede rotation of the rotation shaft <NUM>, resulting in increase in power consumption of the pump body assembly. When the depth h of the avoidance recess <NUM> is greater than <NUM>%-<NUM>% of the height H of the flange structure, the depth of the avoidance recess <NUM> on the positioning boss <NUM> is too large, resulting in decrease in strength of the positioning boss <NUM> and decrease in stability of the pump body assembly during running, and the displacement the rotation shaft <NUM> and the cylinder <NUM>.

In some embodiments, the avoidance recess <NUM> has a depth h equal to <NUM>%-<NUM>% of a height H of the flange structure. Specifically, the depth h of the avoidance recess <NUM> equal to <NUM>%-<NUM>% of the height H of the flange structure is the further definition to the depth h of the avoidance recess <NUM> equal to <NUM>%-<NUM>% of the height H of the flange structure. When the depth h of the avoidance recess <NUM> equals to <NUM>%-<NUM>% of the height H of the flange structure, the avoidance recess <NUM> can effectively enlarge the flow path of the oil liquid, reduce impediment of the oil liquid to the rotation shaft <NUM> during its rotation, and reduce power consumption of the pump body assembly.

The flange structure in the present disclosure comprises a lower flange <NUM>. The rotation shaft <NUM> has a long shaft segment and a short shaft segment, with the long shaft segment having a diameter greater than that of the short shaft segment, such that a rotation shaft support face is formed at an interface between the long shaft segment and the short shaft segment. The rotation shaft support face is supported at the positioning boss <NUM>. The short shaft segment penetrates into the lower flange <NUM>.

Specifically, the second segment <NUM> of the positioning boss <NUM> on the supports the support face of the rotation shaft <NUM>. During rotation of the rotation shaft <NUM>, the avoidance recess <NUM> on the lower flange <NUM> enlarges the flow path of the oil liquid in the cylinder <NUM>, resulting in reduction in impediment of the oil liquid to the rotation shaft <NUM> and reduction in power consumption.

The pump body assembly in the present disclosure further comprises a cylinder sleeve having a volume cavity in which the cylinder <NUM> is rotatably arranged. The cylinder <NUM> is provided, in its radial direction, with a piston hole <NUM>, the piston <NUM> is slidably arranged in the piston hole <NUM>, the rotation shaft <NUM> penetrates through the piston <NUM> and drives the piston <NUM> to reciprocate in an extension direction of the piston hole <NUM>, and the cylinder <NUM> rotates to cause rotation of the piston <NUM>. The flange structure is located at an end of the cylinder sleeve in its axial direction, and at least a portion of the rotation shaft <NUM> penetrates into the flange structure.

Specifically, the cylinder <NUM> in the cylinder sleeve is rotated synchronously with the rotation shaft <NUM>. The piston <NUM> reciprocates in the piston hole <NUM>. The relative movement between the piston <NUM> and the rotation shaft <NUM> enables oil liquid transfer within two flow paths formed by cooperation of the cylinder <NUM>, the piston <NUM> and the rotation shaft <NUM>. The two flow paths increase and decrease periodically with the reciprocating movement of the piston <NUM> to drive oil liquid transfer. The avoidance recess <NUM> disposed on the positioning boss <NUM> of the lower flange <NUM> can reduce impediment of the positioning boss <NUM> to oil liquid flow in the flow path(s), decrease resistance between the rotation shaft <NUM> and the oil liquid, and reduce power consumption of the pump body assembly.

By setting the avoidance recess <NUM> on the positioning boss <NUM>, the impediment of the flange structure to the flow path is reduced and the power consumption of the compressor is reduced. Currently, the flange structure of the prior pump body seriously blocks the lower portion of the flow path in the cylinder <NUM> and the piston <NUM> such that the frozen oil cannot be smoothly transferred in the flow path, resulting in increase in resistance to the rotation shaft <NUM> during rotation and increase in power consumption of the compressor.

Apparently, the embodiments as described above are only some embodiments of the present disclosure, rather than all embodiments. Any other embodiments obtained by those skilled in the art, based on the embodiments in the present disclosure and without any inventive work, will fall within the protection scope of the present disclosure.

It should be noted that the terms as used herein are only for describing specific implementations, and are not intended to limit the exemplary implementations according to the present application. As used herein, the singular form is intended to comprise the plural form, unless otherwise specified in the context. In addition, it should be understood that when the terms of "comprise" and/or "include" are/is used in the present description, it means that there are a feature, a step, an operation, a device, a component, and/or the combinations thereof.

Claim 1:
A pump body assembly for a rotary cylinder compressor, the pump body assembly comprising a rotation shaft (<NUM>) and a piston (<NUM>) provided with a sliding hole (<NUM>), wherein at least a portion of the rotation shaft (<NUM>) penetrates into the sliding hole (<NUM>), so as to divide a portion inside the piston (<NUM>) into two cavities, during rotation of the piston (<NUM>) with the rotation shaft (<NUM>), the two cavities increase and decrease periodically, and the sliding hole (<NUM>) is in sliding fit with the rotation shaft (<NUM>), so that oil liquid is pressed at an inner wall of the sliding hole (<NUM>), and the piston (<NUM>) is provided with a piston communication passage communicated with the sliding hole (<NUM>), so as to fluently transfer the oil liquid between the two cavities;
the pump body assembly being characterised in that in an axial direction of the rotation shaft (<NUM>), the piston (<NUM>) is provided on its end face with a piston communication groove (<NUM>), and the piston communication groove (<NUM>) extends in a sliding direction of the piston (<NUM>) and constitutes the piston communication passage; and
the sliding hole (<NUM>) of the piston (<NUM>) is further provided therein with a flexible groove (<NUM>), the flexible groove (<NUM>) extends in the axial direction of the rotation shaft (<NUM>), and the flexible groove (<NUM>) is communicated at its end with the piston communication groove (<NUM>).