CN214741659U

CN214741659U - Differential rotation fan-shaped piston combination and rotary piston engine

Info

Publication number: CN214741659U
Application number: CN202120089051.1U
Authority: CN
Inventors: 王英俊
Original assignee: Individual
Current assignee: Individual
Priority date: 2021-01-13
Filing date: 2021-01-13
Publication date: 2021-11-16
Anticipated expiration: 2031-01-13

Abstract

The utility model discloses a fan-shaped piston combination of differential rotation contains piston combination A and piston combination second, and these two kinds of piston combinations all include sector and dabber portion, and sector and dabber portion are coaxial, and piston combination first and piston combination second coaxial suit and crisscross setting. The utility model discloses a characterized in that piston combination first's mandrel portion is the hollow straight axle of segmentation, the mandrel portion of piston combination second is the step shaft, the sector of piston combination first and the sector of piston combination second are hollow structure, the internal diameter position of the sector of piston combination first and the internal diameter position of the sector of piston combination second all are equipped with the axial tongue-and-groove, the mandrel portion of piston combination first and the corresponding position of the mandrel portion of piston combination second all are equipped with the axial tenon, sector and mandrel portion pass through the axial tenon and the axial tongue-and-groove is connected. Compared with the existing structure, the structure and the connection mode improve the structural rigidity and provide a processing space for the internal liquid cooling channel, and are favorable for solving the problems of vibration, heat dissipation and lubrication.

Description

Differential rotation fan-shaped piston combination and rotary piston engine

Technical Field

The utility model relates to the technical field of engines, particularly, relate to a fan-shaped piston combination of differential rotation and rotary piston engine.

Background

The rotary piston engine of the present invention can be considered as belonging to a Kaltz differential engine. The differential engine belongs to a special engine. In the engine, the ignited high pressure gas directly pushes the piston to rotate in an accelerating way, so that a connecting rod crank mechanism and an air inlet and outlet valve mechanism are omitted, and the stress of parts is small, so that the engine has the characteristics of small whole volume and light weight, and is particularly suitable for the field of aviation industry. The university of the armored force engineering college at home and the Pan cloud professor of the national defense science and technology university have research on the situation, but no practical application report is seen so far.

SUMMERY OF THE UTILITY MODEL

The traditional Kaltz differential engine has at least two groups of sector pistons coaxially sleeved and arranged in a staggered mode, and the pistons are in cantilever structures. This makes the piston unevenly stressed, susceptible to deformation vibration and difficult to seal. Furthermore, it is difficult to give a specific solution to the heat dissipation and lubrication problems faced by power machines, both with the traditional structure of the kartz differential engine and with the current publications.

An object of the utility model is to overcome prior art not enough, provide a fan-shaped piston combination of differential rotation, solve the problem among the prior art. For a specific piston, compared with a fan-shaped piston with a traditional structure, due to stress balance, under the condition that the outline size is the same and the stress is the same, the maximum deformation and the stress of the traditional mode are respectively delta =0.0236mm and sigma =41.6 MP; the maximum deformation and stress of the piston combination A in the patent are respectively delta =0.0113mm and sigma =30.0MP, and are respectively reduced by 52.1% and 27.9%, and the maximum deformation and stress of the piston combination B in the patent are respectively delta =0.0156mm and sigma =23.1MP A, and are respectively reduced by 33.9% and 44.5%.

The utility model discloses can dispel the heat through traditional piston ring technical method, also can dispel the heat through the liquid cooling mode, wherein in order to realize the liquid cooling mode heat dissipation, must make coolant liquid circulation channel. The structure provided by the utility model can conveniently establish a circulation channel on the machine part in a machining mode.

Aiming at the lubrication problem, a recyclable and reusable lubrication system is the fundamental method for solving the problem of large consumption of lubricating oil. The utility model provides a setting has the sealing ring of accuse oily ability and sets up the lubricating oil recovery hole in cylinder body suitable position and solve this difficult problem.

To sealed problem, except that traditional sealing strip is unexpected, the utility model provides a set up non-contact and seal gas device on the inboard arc surface of piston combination first fan-shaped portion and dabber portion terminal surface junction, including the labyrinth of obturating or the honeycomb structure of obturating. The piston combination is provided by thoroughly decomposing the piston combination when the structural scheme provided by the utility model is not convenient for overhaul.

The utility model discloses a technical characterstic more than realizing through following technical scheme: the utility model discloses a differential rotation fan-shaped piston combination, which comprises a piston combination A and a piston combination B, wherein the piston combination A and the piston combination B both comprise a fan-shaped part and a mandrel part, the fan-shaped part and the mandrel part are coaxial, the transverse section of the fan-shaped part is fan-shaped, the longitudinal section of the fan-shaped part is rectangular, the piston combination A and the piston combination B are coaxially sleeved, the piston combination is characterized in that the mandrel portion of the piston combination A is a segmented hollow straight shaft, the mandrel portion of the piston combination B is a stepped shaft, the fan-shaped portion of the piston combination A and the fan-shaped portion of the piston combination B are of a hollow structure, axial mortises are arranged in the inner diameter position of the fan-shaped portion of the piston combination A and the inner diameter position of the fan-shaped portion of the piston combination B, axial tenons are arranged in the corresponding positions of the mandrel portion of the piston combination A and the mandrel portion of the piston combination B, and the fan-shaped portions and the mandrel portions are connected through the axial mortises and the axial mortises.

Preferably, in order to ensure that the connection between the tenon and the mortise is tight and not loose, interference fit is formed between the axial tenon of the fan-shaped part of the piston combination A and the axial tenon of the core shaft part of the piston combination A, and between the axial tenon of the fan-shaped part of the piston combination B and the axial tenon of the core shaft part of the piston combination B.

Preferably, in order to ensure differential rotation between the two groups of pistons, clearance fit is formed between the inner diameter of the sector part of the piston combination A and the large radius of the mandrel part stepped shaft of the piston combination B, and between the inner diameter of the hollow straight shaft of the mandrel part of the piston combination A and the small radius of the mandrel part stepped shaft of the piston combination B.

Preferably, in order to enable the fan section to have good heat dissipation performance, the core shaft section can bear large torque, the material of the fan section is cast aluminum, and the material of the core shaft section is alloy steel.

Preferably, in order to ensure the sealing performance and the heat dissipation performance, the end face, the inner arc face and the outer arc face of the fan-shaped part are provided with a sealing groove and a sealing strip, and a heat transfer groove and a heat transfer strip. And non-contact air sealing devices are arranged on the inner side arc surface of the fan-shaped part of the piston combination A and the joint of the end surface of the mandrel part, and each air sealing device comprises a sealing labyrinth or a sealing honeycomb structure. The sealing strip also has oil control capacity, and can scrape off redundant lubricating oil on the wall surface of the cylinder so as to recover and recycle the lubricating oil. The specific method is that a lubricating oil recovery hole is arranged at a proper position of the cylinder body, and when the piston sweeps across the recovery hole, the lubricating oil scraped by the sealing strip enters the recovery channel through the lubricating oil recovery hole.

Preferably, in order to enable the engine to bear larger heat load, the mandrel part of the piston combination A is provided with a circular sealing groove and a cooling liquid inlet on the end face matched with the stepped shaft of the mandrel part of the piston combination B, the mandrel part of the piston combination B is provided with a cooling liquid outlet on the end face matched with the mandrel part of the piston combination A, and the circumferential surface of the outer side of the mandrel part of the piston combination B is provided with an annular sealing groove and is provided with a sealing ring.

Preferably, in order to form a complete cooling liquid circulation channel, the axial tenon inner parts of the mandrel parts of the piston combination A and the piston combination B and the fan-shaped parts of the piston combination A and the piston combination B are provided with cooling liquid channels.

Preferably, the cooling fluid is a lubricating oil.

Preferably, the present invention provides a rotary piston engine comprising a differential rotary sector piston combination according to any one of the preceding claims.

The utility model discloses a provide a piston combination of new construction, solved the unbalanced defect of traditional Ka's Alzheimer's differential engine atress. The piston combination of the utility model has high structural rigidity, and can reduce the vibration of parts and the problems caused by the vibration of the parts; the machining space is large, the condition is good, the liquid cooling channel can be machined, the heat load of the engine is convenient to improve, and the advantages in the aspects of size and weight are further strengthened. And simultaneously, the utility model discloses simple structure, the equipment is convenient with low costs, is convenient for use widely on a large scale.

Drawings

FIG. 1 is a schematic view of a conventional Kartz differential engine;

FIG. 2 is a combination view of embodiment 1 of the present invention;

fig. 3 is an exploded view of embodiment 1 of the present invention;

fig. 4 is a schematic view of a sector b of a piston assembly according to embodiment 1 of the present invention;

FIG. 5 is a sealing labyrinth structure of a sector of a piston combination A in embodiment 1 of the invention;

fig. 6 is a schematic view of a second shaft portion of the piston assembly according to embodiment 1 of the present invention;

figure 7 is a sealed honeycomb structure of a piston combination A sector in embodiment 2 of the invention.

Detailed Description

The embodiments of the present invention will be described in detail below, and the present embodiment is implemented on the premise of the technical solution of the present invention, and a detailed implementation manner and a specific operation process are given, but the scope of the present invention is not limited to the following embodiments.

Example 1

Unlike the conventional structure of a Karl differential engine shown in FIG. 1, the piston assembly disclosed in this embodiment 1 includes a piston assembly A and a piston assembly B, as shown in FIGS. 2 and 3. The piston combination A2 and the piston combination B1 respectively comprise a fan-shaped part and a mandrel part, the fan-shaped part and the mandrel part are coaxial, the transverse section of the fan-shaped part is fan-shaped, the longitudinal section of the fan-shaped part is rectangular, and the piston combination A2 and the piston combination B1 are coaxially sleeved, and the piston combination A2 is characterized in that the mandrel part is a segmented hollow straight shaft 21, the mandrel part is a stepped shaft 11, the fan-shaped part 22 of the piston combination A2 and the fan-shaped part 12 of the piston combination B1 are both of a hollow structure, the inner diameter position of the fan-shaped part 22 of the piston combination A2 and the inner diameter position of the fan-shaped part 12 of the piston combination B1 are both provided with

axial mortises

212 and 112,

axial tenons

211 and 111 are respectively arranged at corresponding positions of the mandrel part 21 of the piston combination A2 and the mandrel part 11 of the piston combination B1, and the fan-shaped part 12 and the mandrel part 11 are connected through the axial mortises 111 and the axial mortises 112, the sector 22 and the spindle 21 are connected by an axial tongue 211 and an axial groove 212.

Interference fit is formed between the axial mortise 212 of the sector 22 of the piston assembly A2 and the axial tenon 211 of the spindle portion 21 of the piston assembly A2, and between the axial mortise 112 of the sector 12 of the piston assembly B1 and the axial tenon 111 of the spindle portion 11 of the piston assembly B1.

Clearance fit is formed between the inner diameter of the sector part 22 of the piston combination A2 and the large radius of the stepped shaft of the mandrel part 11 of the piston combination B1, and between the inner diameter of the hollow straight shaft of the mandrel part 21 of the piston combination A2 and the small radius of the stepped shaft of the mandrel part 11 of the piston combination B1.

The material of the fan-shaped part is cast aluminum ZL109, and the material of the mandrel part is 40Cr alloy steel.

As shown in fig. 4, the end face and the inner and outer arc faces of the sector are provided with a sealing groove 1 and a sealing strip (not shown), and a heat transfer groove 2 and a heat transfer strip (not shown). Non-contact air sealing devices, namely sealing labyrinth, are arranged on the inner circular arc surface of the sector part 22 of the piston assembly A2 and the joint of the end surface of the mandrel part 21, as shown in figure 5. The sealing strip also has oil control capacity, can scrape off redundant lubricating oil on the wall surface of the cylinder so as to recover and recycle the lubricating oil, and is similar to a common piston ring.

The mandrel part of the piston combination A2 is provided with a circular sealing groove and a cooling liquid inlet on the end face matched with the stepped shaft of the mandrel part of the piston combination B1, the mandrel part 11 of the piston combination B1 is provided with a cooling liquid outlet on the end face matched with the mandrel part 21 of the piston combination A2, and the circumferential surface of the outer side of the mandrel part 11 of the piston combination B1 is provided with an annular sealing groove and a sealing ring.

As shown in fig. 6, the coolant passage 5 is provided inside the axial tenon of the mandrel portion 21 of the piston assembly a 2 and inside the axial tenon of the mandrel portion of the piston assembly b 1.

The inside of the sector 22 of the piston assembly A2 and the inside of the sector 12 of the piston assembly B1 are provided with cooling fluid channels.

The cooling liquid is lubricating oil.

Example 2

Most technical features of this embodiment are the same as those described in embodiment 1, and the difference is that the gas sealing device disposed on the inner circular arc surface of the sector 22 of the piston assembly a 2 in this embodiment is of a sealing honeycomb structure, as shown in fig. 7, the sealing honeycomb here is in the form of an insert, and is inserted into the inner cavity of the sector 22 of the piston assembly a 2 in the axial direction.

Claims

1. The utility model provides a fan-shaped piston combination of differential rotation, fan-shaped piston combination of differential rotation includes piston combination A and piston combination B, piston combination A and piston combination B all include sector and mandrel portion, the sector with the mandrel portion is coaxial, the transverse section of sector is fan-shaped, the longitudinal section of sector is the rectangle, piston combination A with the coaxial suit of piston combination B, its characterized in that, the mandrel portion of piston combination A is the hollow straight axle of segmentation, the mandrel portion of piston combination B is the step axis, the sector of piston combination A with the sector of piston combination B is hollow structure, the internal diameter position of the sector of piston combination A with the internal diameter position of the sector of piston combination B all is equipped with the axial tongue-and-groove, the mandrel portion of piston combination A with the corresponding position of the mandrel portion of piston combination B all is equipped with the axial tenon head, the sector part and the core shaft part are connected through the axial tenon and the axial mortise.

2. The differential rotary sector piston combination of claim 1, wherein an interference fit is formed between the axial mortise of the sector portion of the piston combination A and the axial tenon of the mandrel portion of the piston combination A; and interference fit is formed between the axial mortises of the fan-shaped part of the piston combination B and the axial tenons of the core shaft part of the piston combination B.

3. A differential rotary sector piston combination as claimed in claim 1 wherein the inner diameter of the sector of piston combination a is in clearance fit with the large radius of the stepped shaft of the mandrel portion of piston combination b; and the inner diameter of the hollow straight shaft of the mandrel part of the piston combination A and the small radius of the stepped shaft of the mandrel part of the piston combination B form clearance fit.

4. A differential rotary sector piston combination as claimed in claim 1 wherein the sector material is cast aluminum and the mandrel portion material is an alloy steel.

5. The differential rotation sector piston combination according to claim 1, wherein the end face and the inner and outer arc faces of the sector are provided with sealing grooves and sealing strips, heat transfer grooves and heat transfer strips, and the inner arc face of the sector of the piston combination A and the joint of the end face of the mandrel are provided with non-contact air sealing devices, wherein the air sealing devices include but are not limited to sealing grates or sealing honeycomb structures.

6. The differential rotary sector piston assembly of claim 1, wherein the mandrel portion of piston assembly a is provided with a circular sealing groove and a coolant inlet on an end surface engaged with the stepped shaft of the mandrel portion of piston assembly b, the mandrel portion of piston assembly b is provided with a coolant outlet on an end surface engaged with the mandrel portion of piston assembly a, and the circumferential surface outside the mandrel portion of piston assembly b is provided with an annular sealing groove and a sealing ring.

7. A differential rotary sector piston combination according to claim 6, wherein coolant passages are provided inside the axial tenon of the spindle portion of piston combination A and inside the axial tenon of the spindle portion of piston combination B.

8. A differential rotary sector piston combination as claimed in claim 6 wherein coolant passages are provided in both the sector interior of piston combination A and the sector interior of piston combination B.

9. A differential rotary sector piston combination as claimed in claim 8 wherein the coolant is a lubricating oil.

10. A rotary piston engine comprising a differential rotary sector piston combination according to any one of claims 1 to 9.